A high-thrust brake for belt conveyor

Abstract

The invention discloses a high-thrust brake for a belt conveyor, comprising an oil cylinder, a transmission arm, a base, a brake shoe and a gate head; the base has two fixed rotating shaft sleeves for installing the transmission arm; there is a pair of transmission arms, which are symmetrically installed on the base through support pins, the rear ends of the two transmission arms are respectively connected to the cylinder bottom and the piston rod end of the oil cylinder, and the front ends of the two transmission arms are respectively installed with the gate head through the gate head pin shaft; there is a pair of brake shoes, which are relatively installed on the gate head; the oil cylinder is divided into a front chamber and a rear chamber before and after the piston, the front chamber is a rod chamber, and the rear chamber is a rodless chamber, the front chamber is connected to the opening oil pipe joint, and the rear chamber is connected to the closing oil pipe joint; the oil pressure in the rear chamber of the oil cylinder is less than the oil pressure in the front chamber, pushing the piston to complete the closing action, and the oil pressure in the rear chamber of the oil cylinder is greater than the oil pressure in the front chamber, pushing the piston to complete the opening action. The invention adopts a single oil cylinder, a double transmission arm, and changes the direct-acting structure to a parallel lever mechanism, which can quickly provide a large braking force, achieve safe braking, and avoid accidents.

Description

Technical Field

[0001] The invention relates to a braking device for a mining belt conveyor, in particular to a large-thrust brake for a belt conveyor, and belongs to the technical field of belt conveyor braking. Background Art

[0002] The brake is an important component to ensure the safe and normal operation of the belt conveyor. During the operation of the belt conveyor, the brake is used to brake the belt conveyor drive roller to prevent the belt from sliding under the action of inertia and friction when the belt conveyor stops; or to reduce the speed of the running mechanism and finally stop moving; in special cases, the movement speed is adjusted by promoting the balance between braking force and gravity. Brakes are generally divided into high-speed brakes and low-speed brakes. High-speed brakes are small braking torque brakes used on high-speed shafts (motor and reducer shafts); low-speed brakes are large braking torque brakes used on low-speed machines (reducer shafts and drum shafts). They can be widely used in large and medium-sized belt conveyors, hoists, etc. using disc brakes to achieve parking and parking brakes to ensure the safe operation of the equipment.

[0003] At present, the most commonly used brakes for mining belt conveyors adopt a normally closed design, including brake heads, brake discs, hydraulic stations, electric control boxes, control systems, etc., which have the advantages of large braking torque, adjustable braking force, sensitive operation, good heat dissipation performance, safe and reliable operation, and convenient use and maintenance. Conventional brake heads include brake heads, brake shoes, bases, oil cylinders, disc springs, transmission arms, etc. The braking force relies on the disc spring to apply force to brake, and a hydraulic drive release device is required. It is safe and reliable, sensitive to operation, and has a short closing (brake) time. However, when the belt conveyor is running, the brake head is required to open at the moment the motor starts; when the belt conveyor stops, the brake head is closed under the action of inertia for a short time, and the braking force is only driven by the brake disc spring. It cannot quickly form sufficient positive pressure, and the braking torque is applied smoothly. The brake disc rubs against the brake head brake shoe to generate a lot of heat, which makes the brake disc temperature rise, or the braking time is too long, and it is likely that the brake cannot be completely braked, resulting in serious accidents such as flying and slipping. Summary of the invention

[0004] In view of the above existing technical problems, the present invention provides a high-thrust brake for a belt conveyor, which is intended to quickly provide a large braking force, achieve safe braking, and avoid the occurrence of serious production accidents.

[0005] To achieve the above-mentioned purpose, the present invention provides a high-thrust brake for a belt conveyor, comprising an oil cylinder, a transmission arm, a base, a brake shoe and a gate head; the base has two fixed rotating shaft sleeves for installing the transmission arm; the transmission arms are provided in a pair, which are symmetrically installed on the base through support pins, the rear ends of the two transmission arms are respectively connected to the cylinder bottom and the piston rod end of the oil cylinder, and the front ends of the two transmission arms are respectively installed with the gate heads through the gate head pins; the brake shoes are provided in a pair, which are relatively installed on the gate heads; the oil cylinder is divided into a front chamber and a rear chamber before and after the piston, the front chamber is a rod chamber, and the rear chamber is a rodless chamber, the front chamber is connected to a gate opening oil pipe joint, and the rear chamber is connected to a gate closing oil pipe joint; the oil pressure in the rear chamber of the oil cylinder is less than the oil pressure in the front chamber, which pushes the piston to complete the gate closing action, and the oil pressure in the rear chamber of the oil cylinder is greater than the oil pressure in the front chamber, which pushes the piston to complete the gate opening action.

[0006] The beneficial effect of adopting the above technical scheme is that the existing brake system mostly adopts the direct action of the oil cylinder to open the gate, the oil pressure is reduced, and the disc spring is reset to close the gate. In the existing brake system, the brake heads must be used in pairs, and the double-headed studs are used to fix the connection in the middle. The large thrust brake head adopts a single oil cylinder and a double transmission arm, and the direct action structure is changed to a parallel lever mechanism. The disc spring reset drives the transmission arm to close the gate. When the large thrust brake head fixed integrated structure of the invention is installed, it only needs to fix the base connection bolt hole, and the symmetrical transmission arm is automatically aligned without the brake disc wearing. Because the oil cylinder is divided into two parts by the piston, one side of the piston is a rod cavity and the other side is a rodless cavity. In this way, there is a difference in the size of the force area on both sides of the piston. If the thrust on both sides of the oil cylinder is to be balanced and equal, the applied pressure is inversely proportional to the force area, that is, when the brake is opened, the oil cylinder needs a large oil pressure to act on the rod cavity to complete the opening action. When the brake is closed, the oil pressure in the front cavity of the oil cylinder decreases, and the oil pressure in the rear cavity of the oil cylinder can push the piston to complete the closing action as long as it is less than the oil pressure in the front cavity.

[0007] The present invention further comprises that the front chamber of the oil cylinder is connected to the hydraulic main circuit through an opening oil pipe joint, the rear chamber of the oil cylinder is connected to the hydraulic auxiliary circuit through a closing oil pipe joint, and the hydraulic auxiliary circuit is connected to the hydraulic main circuit through a pressure reducing valve; the hydraulic auxiliary circuit comprises a rear chamber non-return valve and a closing accumulator connected to the closing oil pipe joint, and the rear chamber non-return valve is respectively connected to the closing accumulator and the pressure reducing valve; the hydraulic main circuit comprises a flameproof three-phase asynchronous motor, a gear pump, a front chamber non-return valve connected to the opening oil pipe joint, a disc brake, a flameproof electromagnetic reversing valve, throttle valve, relief valve and secondary relief valve; the flameproof three-phase asynchronous motor is connected to the gear pump, and the flameproof three-phase asynchronous motor is connected to the oil tank through a mesh oil filter; one end of the front cavity one-way valve is connected to the gear pump, and the other end is connected to the disc brake, flameproof electromagnetic reversing valve, accumulator and pressure reducing valve respectively through a paper oil filter; one end of the relief valve is connected to the oil tank, and the other end is connected to pressure gauge one; one end of the throttle valve is connected to the oil tank, and the other end is respectively connected to the flameproof electromagnetic reversing valve and the secondary relief valve, and the secondary relief valve is connected to pressure gauge two.

[0008] The beneficial effect of adopting the above technical solution is that the existing brake device uses a disc spring mechanical reset to close the gate, while the present invention adopts an additional auxiliary oil circuit, and the main oil circuit and the auxiliary circuit are respectively connected to the oil inlets of the front and rear chambers of the oil cylinder through a pressure reducing valve. When the hydraulic oil pressure in the front and rear chambers of the oil cylinder is unbalanced, the piston moves horizontally. Even if the piston is improperly sealed and the hydraulic oil in the front and rear chambers leaks, since the hydraulic main circuit and the hydraulic auxiliary circuit are both connected to accumulators, the front and rear chambers can also automatically replenish hydraulic oil to ensure the stability of the hydraulic oil pressure on both sides of the piston, thereby not affecting the actual action of the brake head and improving the reliability of the system. The system oil pressure can be set at any time in the front and rear chambers of the oil cylinder. The front and rear chambers are both hydraulically driven pistons. The pressure can be controlled within a certain range and can be adjusted linearly with the oil pressure. The system oil pressure can be set at any time through the main circuit overflow valve and the auxiliary circuit through the pressure reducing valve.

[0009] There is an accumulator in the main hydraulic circuit for the gate opening pipeline. When a sudden power failure occurs, the hydraulic oil is pushed out of the accumulator through the bladder filled with compressed nitrogen to achieve slow oil return, ensuring that the gate is slowly closed after a certain delay, which can prevent the inertia force of the belt conveyor from slipping and tearing the belt when the sudden gate closing stops. The auxiliary hydraulic circuit includes an accumulator for the gate closing pipeline. When the gate opening signal is switched to the gate closing signal, the hydraulic oil in the front chamber of the oil cylinder slowly returns, the pressure becomes low, and the oil pressure in the rear chamber is in the accumulator filled with compressed nitrogen to push the hydraulic oil out of the accumulator through the bladder, achieving slow gate closing until the brake completes the braking of the brake disc.

[0010] The present invention further provides that the oil cylinder comprises a cylinder barrel, a cylinder head connected to the cylinder barrel, a cylinder bottom connected to the cylinder barrel, a piston disposed in the cylinder barrel, a piston rod connected to the piston, and a guide sleeve sleeved on the piston rod.

[0011] The beneficial effects of adopting the above technical solution are: the oil cylinder structure is compact and the cylinder barrel volume can be made smaller, which not only saves the installation space of the equipment, but also saves the installation cost.

[0012] The present invention further provides a nut and an O-type rubber seal ring between the cylinder cover and the cylinder barrel, a guide belt and a Y-shaped ring for a piston rod sealing groove between the cylinder cover and the outer end of the piston rod, an O-type rubber seal ring between the piston rod and the piston, and a piston DAS combined seal ring and a guide ring between the piston and the cylinder barrel.

[0013] The beneficial effect of adopting the above technical solution is: good sealing effect.

[0014] Furthermore, the front end of the piston rod is connected to an adjusting rod via a hexagonal thin nut, and the adjusting rod is hinged with an adjusting block.

[0015] The beneficial effects of adopting the above technical solution are: setting an adjusting rod facilitates adjusting the installation distance of the oil cylinder, and the adjusting rod is hinged with the adjusting block, which can bear a larger thrust and transmit it to the transmission arm, the brake head and the brake shoe.

[0016] Furthermore, the present invention, the adjusting block and the cylinder bottom are respectively connected to the transmission arm via a pin shaft, and the cylinder pin shaft and the adjusting block pin shaft are both connected with a baffle.

[0017] The beneficial effect of adopting the above technical solution is that the cylinder bottom is connected to the baffle through the pin shaft, which can mainly prevent the cylinder pin shaft and the adjustment block pin shaft from falling out of the transmission arm.

[0018] According to a further feature of the present invention, the brake shoe is pressed and fixed on its upper and lower surfaces by a pressure plate.

[0019] The beneficial effect of adopting the above technical solution is that the function of the pressure plate is to press the brake shoe to prevent the brake shoe from falling out of the gate head.

[0020] According to the present invention, a mounting hole is provided on the cylinder bottom, and a copper sleeve is provided on the mounting hole.

[0021] The beneficial effect of adopting the above technical solution is that the copper sleeve functions to reduce useless friction resistance between the oil-free lubrication cylinder pin and the cylinder.

[0022] According to the present invention, the valve closing oil pipe joint is connected to a mining pressure sensor.

[0023] The present invention further provides that the valve-opening oil pipe joint is connected to a second mining pressure sensor.

[0024] The beneficial effects of adopting the above technical solution are: the pressure sensor transmits the detected pressure signal to the electric control box in real time, the electric control box program automatically controls the start and stop of the hydraulic system oil pump motor and the action and direction of the solenoid valve. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 It is a structural stereoscopic schematic diagram of the present invention;

[0026] Figure 2 It is a front view of the present invention;

[0027] Figure 3 The present invention Figure 2 Middle AA view;

[0028] Figure 4 It is a left side view of the present invention;

[0029] Figure 5 It is a three-dimensional diagram of the oil cylinder of the present invention;

[0030] Figure 6 It is a main cross-sectional view of the oil cylinder of the present invention;

[0031] Figure 7 It is the hydraulic principle diagram of the present invention;

[0032] Figure 8 It is a structural schematic diagram of the electric control box of the present invention;

[0033] In the figure: 1, base, 2, transmission arm, 3, oil cylinder, 4, adjustment block, 5, gate head pin, 7, support pin, 11, brake shoe, 12, gate head, 13, baffle, 14, pressure plate;

[0034] 22. Piston rod, 23. Cylinder barrel, 24. Piston, 25. Adjusting rod, 26. Copper sleeve, 27. Hexagonal thin nut, 28. Y-ring for piston rod sealing groove, 29. Guide belt, 210. O-type rubber seal ring 1, 211. Cylinder bottom, 212. Guide sleeve, 213. Piston DAS combined seal ring, 214. Guide ring, 215. O-type rubber seal ring 2, 216. Pressure nut;

[0035] 31. Mesh oil filter, 32. Flameproof three-phase asynchronous motor, 33. Gear pump, 34. Front chamber non-return valve, 35. Paper oil filter, 36. Overflow valve, 37. Throttle valve, 38. Flameproof electromagnetic reversing valve, 39. Pressure gauge, 310. Accumulator, 311. Shuttle valve, 312. Disc brake, 313. Mining pressure sensor 1, 314. Pressure reducing valve, 315. Secondary overflow valve, 316. Rear chamber non-return valve, 317. Shut-off accumulator, 318. Mining pressure sensor 2, 319. Pressure gauge 2. DETAILED DESCRIPTION

[0036] The present invention is further described below in conjunction with the accompanying drawings. In the description of the present invention, it should be understood that the directions or positional relationships indicated by the front, side, top, etc. are based on the physical positional relationships of the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific direction, or a specific structure and operation, and therefore cannot be understood as a limitation of the present invention.

[0037] like Figures 1 to 4 As shown, a high-thrust brake for a belt conveyor of the present invention comprises an oil cylinder 3, a transmission arm 2, a base 1, a brake shoe 11 and a gate head 12; the base 1 has two fixed rotating shaft sleeves for installing the transmission arm 2; the transmission arm 2 has a pair, which are symmetrically installed on the base 1 through support pins 7, the rear ends of the two transmission arms 2 are respectively connected to the cylinder bottom 21 and the piston rod end of the oil cylinder 3, and the front ends of the two transmission arms 2 are respectively installed with the gate head 12 through the gate head pin 5; the brake shoe 11 has a pair, which are relatively installed on the gate head 12; the oil cylinder 3 is divided into a front chamber and a rear chamber before and after the piston, the front chamber is a rod chamber, and the rear chamber is a rodless chamber, the front chamber is connected to the opening oil pipe joint, and the rear chamber is connected to the closing oil pipe joint; the oil pressure in the rear chamber of the oil cylinder 3 is less than the oil pressure in the front chamber, which pushes the piston to complete the closing action, and the oil pressure in the rear chamber of the oil cylinder 3 is greater than the oil pressure in the front chamber, which pushes the piston to complete the opening action. Since the oil cylinder is divided into two parts by the piston, one side of the piston is the rod chamber and the other side is the rodless chamber, so there is a difference in the size of the force-bearing area on both sides of the piston. If the thrust on both sides of the oil cylinder is to be balanced and equal, the applied pressure is inversely proportional to the force-bearing area, that is, when the brake is opened, the oil cylinder needs a large oil pressure to act on the rod chamber to complete the opening action. When the brake is closed, the oil pressure in the front chamber of the oil cylinder decreases, and the oil pressure in the rear chamber of the oil cylinder can push the piston to complete the closing action as long as it is less than the oil pressure in the front chamber.

[0038] Another embodiment of the present invention is as follows Figure 7As shown, the front chamber of the oil cylinder 3 is connected to the hydraulic main circuit through the opening oil pipe joint, the rear chamber of the oil cylinder 3 is connected to the hydraulic auxiliary circuit through the closing oil pipe joint, and the hydraulic auxiliary circuit is connected to the hydraulic main circuit through the pressure reducing valve 314; the hydraulic auxiliary circuit includes a rear chamber check valve 316 and a closing accumulator 317 connected to the closing oil pipe joint, and the rear chamber check valve 316 is connected to the closing accumulator 317 and the pressure reducing valve 314 respectively; the hydraulic main circuit includes a flameproof three-phase asynchronous motor 32, a gear pump 33, a front chamber check valve 34 connected to the opening oil pipe joint, a disc brake 312, a flameproof electromagnetic reversing valve 38, a throttle valve 37, and a relief valve 314. 6 and a secondary relief valve 315; the flameproof three-phase asynchronous motor 32 is connected to a gear pump 33, and the flameproof three-phase asynchronous motor 32 is connected to a fuel tank through a mesh oil filter 31; one end of the front chamber one-way valve 34 is connected to the gear pump 33, and the other end is respectively connected to a disc brake 312, a flameproof electromagnetic reversing valve 38, an accumulator 310 and a pressure reducing valve 314 through a paper oil filter 35; one end of the relief valve 36 is connected to the fuel tank, and the other end is connected to a pressure gauge 39; one end of the throttle valve 37 is connected to the fuel tank, and the other end is respectively connected to a flameproof electromagnetic reversing valve 38 and a secondary relief valve 315, and the secondary relief valve 315 is connected to a pressure gauge 319. When the hydraulic oil pressure in the front and rear chambers of the oil cylinder is unbalanced, the piston moves horizontally. Even if the piston seal is improper and the hydraulic oil in the front and rear chambers leaks, since the hydraulic main circuit and the hydraulic auxiliary circuit are connected to accumulators, the front and rear chambers can automatically replenish hydraulic oil to ensure the stability of the hydraulic oil pressure on both sides of the piston, thereby not affecting the actual action of the brake head and improving the reliability of the system. The system oil pressure can be set at any time in the front and rear chambers of the oil cylinder. The front and rear chambers are hydraulically driven pistons. The pressure can be controlled within a certain range and can be adjusted linearly with the oil pressure. The system oil pressure can be set at any time through the main circuit overflow valve and the auxiliary circuit through the pressure reducing valve.

[0039] In addition, there is an accumulator in the main hydraulic circuit for the gate opening pipeline. When a sudden power failure occurs, the hydraulic oil is pushed out of the accumulator through the bladder filled with compressed nitrogen to achieve slow oil return, ensuring that the gate is slowly closed after a certain delay, which can prevent the inertia force of the belt conveyor from slipping and tearing the belt when the sudden gate closing stops. The auxiliary hydraulic circuit includes an accumulator for the gate closing pipeline. When the gate opening signal is switched to the gate closing signal, the hydraulic oil in the front chamber of the oil cylinder slowly returns, the pressure becomes low, and the oil pressure in the rear chamber is pushed out of the accumulator through the bladder filled with compressed nitrogen to achieve slow gate closing until the brake completes the braking of the brake disc.

[0040] Another embodiment of the present invention is as follows Figure 5 and Figure 6As shown, the oil cylinder 3 comprises a cylinder barrel 23, a cylinder head connected to the cylinder barrel 23, a cylinder bottom 211 connected to the cylinder barrel 23, a piston 24 disposed in the cylinder barrel 23, a piston rod 22 connected to the piston 24, and a guide sleeve 212 sleeved on the piston rod 22. The oil cylinder has a compact structure and the cylinder barrel can be made smaller, which not only saves the installation space of the equipment, but also saves the installation cost.

[0041] Another embodiment of the present invention is as follows Figure 6 As shown, a nut 216 and an O-type rubber sealing ring 210 are provided between the cylinder cover and the cylinder barrel 23, a guide belt 29 and a Y-shaped ring 28 for the piston rod sealing groove are provided between the cylinder cover and the outer end of the piston rod 22, an O-type rubber sealing ring 215 is provided between the piston rod 22 and the piston 24, and a piston DAS combined sealing ring 213 and a guide ring 214 are provided between the piston 24 and the cylinder barrel 23.

[0042] Another embodiment of the present invention is as follows Figure 1 and Figure 5 As shown, the front end of the piston rod 22 is connected to the adjusting rod 25 through a hexagonal thin nut 27, and the adjusting rod 25 is hinged with an adjusting block 4. The adjusting rod 25 is arranged to facilitate the adjustment of the cylinder installation distance. The adjusting rod 25 is hinged with the adjusting block 4, and can bear a larger thrust to be transmitted to the transmission arm 2, the brake head 12, and the brake shoe 11.

[0043] Another embodiment of the present invention is as follows Figure 1 As shown, the adjusting block 4 and the cylinder bottom 211 are respectively connected to the transmission arm 2 through a pin shaft, and the cylinder pin shaft and the adjusting block pin shaft are both connected with a baffle 13. The cylinder bottom 211 is connected to the baffle 13 through the pin shaft to mainly prevent the cylinder pin shaft and the adjusting block pin shaft from falling out of the transmission arm.

[0044] Another embodiment of the present invention is as follows Figure 1 As shown, the upper and lower surfaces of the brake shoe 11 are pressed and fixed by a pressing plate 14. The function of the pressing plate 14 is to press the brake shoe 11 tightly to prevent the brake shoe 11 from escaping from the gate head 12.

[0045] Another embodiment of the present invention is as follows Figure 6 As shown, the cylinder bottom 211 is provided with a mounting hole, and a copper sleeve 26 is arranged on the mounting hole. The function of the copper sleeve 26 is to reduce useless friction resistance between the oil-free lubricating cylinder pin 6 and the oil cylinder 3.

[0046] Another embodiment of the present invention is as follows Figure 7 As shown, the oil pipe joint for closing the gate is connected to a mine pressure sensor 1 313, and the oil pipe joint for opening the gate is connected to a mine pressure sensor 2 318. The pressure sensor transmits the detected pressure signal to the electric control box in real time, and the electric control box program automatically controls the start and stop of the hydraulic system oil pump motor and the action reversal of the solenoid valve.

[0047] When in use, the brake is installed on a disc brake with the following installation implementation requirements:

[0048] A. For disc brakes with bearing support, the installation requirements are relatively low, that is, the coaxiality of the input shaft and the center line of the connected roller should be less than 0.1mm, and the foundation should be fixed.

[0049] B. For disc brakes, the brake disc is directly hung on the transmission drum shaft through a coupling. This form has low cost, but the on-site installation is cumbersome and has high requirements.

[0050] B1. Move the entire disc brake assembly to the installation location and remove the brake head, or remove it together with the support.

[0051] B2. Install the coupling and the brake disc together on the drum. Pay attention to the connection method, some are key connections, some are expansion sleeve connections. Apply butter on the expansion sleeve and tighten the screws.

[0052] B3. Boost the brake and turn the adjusting screw of the brake head clockwise to facilitate the installation of the brake head.

[0053] B4. Install the brake head on the support.

[0054] B5. Base for coarse adjustment disc brake.

[0055] B6. Increase pressure to release the brake, turn the adjusting screw of the brake head counterclockwise, and adjust the brake shoe to fit tightly against the gate disc.

[0056] B7. Adjust the screw in the reverse direction until there is 1-2mm between the brake shoe and the brake disc, then stop.

[0057] B8. Adjust the base of the disc brake to make the clearances between the brake heads equal, then tighten the anchor bolts and release the pressure.

[0058] In addition, when installing the disc brake, ensure that the brake shoe 11 of the brake head is centered and there should be no large offset. In addition, the hydraulic station should be placed near the disc brake. The hydraulic station uses hydraulic oil, and the oil level should be above the middle of the oil level gauge, preferably at 2 / 3. When filling the oil, it must be filled through the air filter and its purity must be ensured. The electric control box should be placed where the brake and the hydraulic station can be seen. The wiring must not be wrongly connected or loosely connected.

[0059] In addition, the brake using this brake head has the following installation requirements when implemented:

[0060] The hydraulic station is mainly composed of the hydraulic part of the system, including high-pressure hose, gear pump 33, flameproof three-phase asynchronous motor 32, check valve 34, valve station, accumulator 310, pressure reducing valve 314, etc. The oil pump used in the hydraulic station is a standard gear pump, the maximum system pressure is 20MPa, and the flow rate is 14L / min. The oil tank capacity of the hydraulic station is 240L. The gear pump 33 receives the power of the flameproof three-phase asynchronous motor 32, draws hydraulic fluid from the oil tank, and delivers it to the valve station on the hydraulic station. The valve station is mainly composed of an integrated block, a relief valve 36, a secondary relief valve 315, a front chamber check valve 34 and a flameproof electromagnetic reversing valve 38. Both relief valves are safety relief valves.

[0061] 1. The implementation of the hydraulic part of this system must strictly follow the hydraulic principle Figure 7 The operation process is as follows:

[0062] 1-1. Check whether the oil level of the oil tank 31 meets the requirements. Observe the oil level gauge at one end of the oil tank 31. The normal oil level should be at 2 / 3 of the oil level gauge. If the oil level is too low, it is easy to cause oil suction difficulty or empty suction, causing malfunction.

[0063] 1-2. Check the rotation direction of the flameproof three-phase asynchronous motor 32. The gear pump 33 is a right-handed pump, and the rotation direction of the flameproof three-phase asynchronous motor 32 must be consistent with that of the gear pump 33.

[0064] 1-3. Check whether the pipeline connection is correct.

[0065] 1-4. Loosen the overflow valve 36 on the integrated block to the bottom.

[0066] 1-5. Start the gear pump 33, slowly turn the relief valve 36, observe the pressure gauge 39, and when the oil pressure gradually increases to the specified 10MPa high pressure upper limit, close the relief valve 36. Adjust the pressure reducing valve 314 so that the oil pressure gradually increases to the specified 6MPa, and lock the fastening nut.

[0067] 1-6. Loosen the secondary relief valve 315 on the integrated block to the bottom.

[0068] 1-7. Start the gear pump 33, switch to the semi-brake mode, slowly turn the secondary relief valve 315, observe the pressure gauge 319, and when the oil pressure gradually increases to the specified upper limit of 3-8 MPa, prepare the secondary relief valve 315.

[0069] 1-8. Before each shutdown, adjust the throttle valve 37 on the oil return pipe, measure the closing time to ensure it is within the allowable time, and lock the nut of the throttle valve 37.

[0070] 1-9. When the machine is shut down, the hydraulic oil in the front chamber of the oil cylinder 3 returns to the oil tank 31 through the throttle valve 37. Under the action of the closing accumulator 317, the hydraulic oil enters the rear chamber of the oil cylinder 3, pushing the brake head to close the gate.

[0071] 1-10. Check the nitrogen pressure of the gate accumulator 317 regularly before working. When the gas pressure is lower than the set gas pressure, use a nitrogen bottle connection tool with a higher gas pressure than the used gas pressure to inflate and pressurize the gate accumulator 317.

[0072] During the above implementation process, check that there is no leakage in the pipeline. After the implementation process is completed, the valves on the valve station shall not be twisted or moved at will.

[0073] 2. The operation process of the electronic control part of this system is as follows:

[0074] For the brake, whether it is up-moving, down-moving, on the ground or underground, the brake body and the electric control box are the same. The hydraulic station is divided into two working modes: up-moving and down-moving. The main difference is that the down-moving mode has an additional electromagnetic reversing action compared to the up-moving mode, which is used to achieve belt semi-braking when the down-moving belt conveyor is overspeeding. The electric control is divided into four modes: underground up-moving, underground down-moving, ground up-moving, and ground down-moving. Among them, ground down-moving is less used and is not considered for the time being. The following describes them separately.

[0075] 2-1. The electronic control part of the underground upward disc brake:

[0076] This system uses PLC as the control core, and realizes manual and automatic complex control through software programming. It has simple circuits, stable control, high reliability, easy upgrade or transformation, low failure rate, long service life, and easy maintenance. It can easily realize communication connection with the main control system of the belt conveyor, so this system has the function of remote control on the basis of short-range control, and is easy to operate.

[0077] like Figure 8 As shown, there is a corresponding switch on the electric control box. Selecting the "off" position means the power is disconnected, and selecting the "on" position means the power is connected.

[0078] There is a control method switch. Select the "manual" position for local single-step control, select "remote control" for automatic remote control, and select "near control" for local automatic control.

[0079] 2-1-1. Manual operation: Press the buttons on the operation panel to manually start the oil pump, open the solenoid valve, stop or reset the fault.

[0080] Manually operate the flameproof three-phase asynchronous motor 32 and the gear pump 33 to start, and then control the flameproof electromagnetic reversing valve 38 to start. At this time, the oil pressure rises and the disc brake slowly opens; when the oil pressure rises to 8MPa, the disc brake is fully opened. Press the stop button, the flameproof three-phase asynchronous motor 32, the gear pump 33, and the flameproof electromagnetic reversing valve 38 stop, the pressure slowly drops to 0MPa, and the disc brake is completely closed, and the disc brake is in a braking state.

[0081] 2-1-2. Automatic operation: divided into short-range control and long-range control.

[0082] 2-1-2-1. Remote control automatic operation: Select the "remote control" position to start remote automatic control, and the short-range control is invalid. The system automatically runs according to the logical sequence of the program design, without manual single-step operation.

[0083] The logical sequence of automatic operation is as follows: after receiving the "automatic start" signal from the main control, the system starts the flameproof three-phase asynchronous motor 32 and gear pump 33 first, delays 2S to start the flameproof electromagnetic reversing valve 38, and sends a start signal to the main control when the oil pressure slowly rises to 8MPa; the pressure continues to rise to 10MPa, and the flameproof three-phase asynchronous motor 32 and gear pump 33 are stopped for 2 minutes to maintain the pressure; if the pressure drops below 8MPa, the system will start the flameproof three-phase asynchronous motor 32 and gear pump 33 to automatically replenish the pressure until the pressure reaches the upper limit of the pressure maintenance value. The system will monitor the entire pressure maintenance and pressure replenishment process in real time to ensure the normal operation of the belt conveyor. When stopping, the main control sends a "stop" signal to the disc brake control system, the system stops the flameproof three-phase asynchronous motor 32, gear pump 33 and flameproof electromagnetic reversing valve 38, and the disc brake slowly closes; wait for the next start.

[0084] 2-1-2-2. Local control automatic operation: When the knob switch is turned to the "local" position, the system enters the process automatic control mode, and the remote control is invalid at this time. The system automatically runs according to the logical sequence of the program design, and no manual single-step operation is required (local operation is generally used for debugging and emergency manual control).

[0085] The human-machine dialogue is displayed as LED indicators, with a total of 6 indicators (2 of which are used as spares). From left to right in the upper row are the oil pump (green), solenoid valve (green), normal operation (green) indicator, and fault indicator (red).

[0086] When a system fault occurs, the fault indicator light will flash and send a fault signal to the main control. After the fault is eliminated, press the "Stop" button to reset, release the fault alarm state, and wait for the next start.

[0087] 2-1-3. Performance characteristics: The electronic control system of the underground upward disc brake has the function of automatic pressure replenishment during normal operation, and has a pressure loss protection function, and can automatically stop when a fault occurs.

[0088] 2-2. Electric control part of the ground disc brake:

[0089] The operating procedures of the ground disc brake and the underground disc brake are roughly the same. The only difference is that the ground disc brake omits the connection with the explosion-proof switch cabinet that controls the oil pump. The other operating procedures are the same as the underground disc brake operating procedures.

[0090] 2-3. Electric control part of underground disc brake:

[0091] The electrical system of underground disc brake is relatively complex. Generally speaking, as long as the power margin of the main motor of the down-conveying belt conveyor is large enough (Kd≥1.3), there is no need to consider the problem of belt overspeed. If the power margin of the main motor of the belt conveyor is less than 1.3, the belt conveyor may be overspeeding, and braking should be performed according to the situation.

[0092] This system uses PLC as the control core, and realizes manual and automatic control of disc brakes through software programming. It has simple circuits, stable control, high reliability, easy upgrade or transformation, low failure rate, long service life, and easy maintenance. It can easily realize communication connection with the main control system of the belt conveyor, so this system has the function of remote control on the basis of short-range control, and is easy to operate.

[0093] Select the "off" position for power off state, select the "on" position for power on state.

[0094] Select the "manual" position for local single-step control, select the "remote control" position for automatic remote control, and select the "near control" position for local automatic control.

[0095] 2-3-1. Manual operation: Press the buttons on the operation panel to manually start the oil pump, open the solenoid valve, control the proportional valve and stop (fault reset) the action.

[0096] 2-3-2. Automatic operation: divided into short-range control and long-range control.

[0097] 2-3-2-1. Remote control automatic operation: Select the switch to the "remote control" position to start the remote automatic control, and the local control is invalid. The system automatically runs according to the logical sequence designed by the program, and no manual single-step operation is required.

[0098] The logical sequence of automatic operation is as follows: after receiving the "auto start" signal from the main control, the system starts the oil pump motor and delays for 2s to start the solenoid valve 1. When the oil pressure rises to 8MPa, the main control sends a start signal; at this time, the pressure continues to rise to 10MPa and the oil pump is stopped for 2 minutes to maintain the pressure; if the pressure drops to 8MPa, the oil pump will automatically replenish the pressure until the pressure reaches the upper limit of the pressure maintenance value. If the power margin of the main motor Kd<1.3, the belt may overspeed, and the disc brake needs to be used to slow down. The specific steps are as follows:

[0099] ①When the speed sensor detects that the belt is overspeeding, the system will automatically turn on the oil pump and switch the solenoid valve at the same time;

[0100] ② After a delay of 2s, open the solenoid valve 2 and adjust the opening of the throttle valve to slowly brake the disc brake until the belt reaches the normal operating speed. Then the system enters the pressure maintaining state to restore the system pressure to the normal operating value.

[0101] When parking, the main control sends a "stop" signal to the disc brake control system, the system stops the oil pump and solenoid valve 1, the disc brake slowly closes, and the system enters standby mode waiting for the next start.

[0102] 2-3-2-2. Local control automatic operation: Select the "local control" position to start local automatic control, and remote control is invalid at this time. The system automatically runs according to the logical sequence of the program design, and no manual single-step operation is required. The main difference between local control automatic and remote control automatic here is that the local control automatic mode will directly enter the pressure holding state after the disc brake is opened, and the belt overspeed judgment will not be performed (local control operation is generally used for debugging and emergency manual control).

[0103] When a system failure occurs, the screen will display the fault beating status and send a fault signal to the main control. After the failure is eliminated, press the "Stop" button to reset, remove the fault status display, and wait for the next start.

[0104] 2-3-3. Performance characteristics: The underground disc brake electronic control system has the function of automatic pressure replenishment and overspeed braking during normal operation, and has a pressure loss protection function, and automatically stops when a fault occurs.

[0105] In addition, on-site debugging should be carried out according to the debugging manual. The specific operations are as follows:

[0106] 1) Before installation and debugging, check whether the circuits of the control cabinet are loose or falling off during transportation.

[0107] 2) Use the manual function to start each action and check whether the power output of the solenoid valve is normal. Whether the pressure rises and falls as required. The specific steps are as follows:

[0108] 2a) Move the solenoid valve in manual position, and you can see the solenoid valve on the screen changes from stopped to working. At the same time, use the multimeter with AC500V voltage range to measure the line voltage connected to the solenoid valve. At this time, there is a voltage of about 127V, which means it is correct.

[0109] 2b) In manual position, move the proportional valve. The proportional valve on the display changes from stopped to working. Use a multimeter with the DC 10A setting to measure the output current of the proportional valve control line. If it changes between 0 and 840mA, it is normal.

[0110] 3) Then, connect the wires of the solenoid valve and the proportional valve, set the control parameters in the industrial control panel, turn SA2 to the "local" position, and observe the status of system pressure increase and pressure relief. If it is normal, you can proceed to the next step.

[0111] 4) Select "Remote Control" to enter the remote control state and the debugging is completed.

[0112] It should be further noted that the specific embodiments described herein are merely examples of the spirit of the present invention. A person skilled in the art of the present invention may make various modifications or additions to the specific embodiments described or replace them in a similar manner without departing from the spirit of the present invention or the scope defined in the claims.

Claims

1. A high-thrust brake for a belt conveyor, characterized in that: It includes an oil cylinder, a transmission arm, a base, a brake shoe and a gate head; the base has two fixed rotating shaft sleeves for installing the transmission arm; there is a pair of transmission arms, which are symmetrically installed on the base through supporting pins, the rear ends of the two transmission arms are respectively connected to the cylinder bottom and the piston rod end of the oil cylinder, and the front ends of the two transmission arms are respectively installed on the gate head through the gate head pin; there is a pair of brake shoes, which are relatively installed on the gate head; the oil cylinder is divided into a front chamber and a rear chamber before and after the piston, the front chamber is a rod chamber, and the rear chamber is a rodless chamber, the front chamber is connected to the opening oil pipe joint, and the rear chamber is connected to the closing oil pipe joint; the oil pressure in the rear chamber of the oil cylinder is less than the oil pressure in the front chamber, which pushes the piston to complete the closing action, and the oil pressure in the rear chamber of the oil cylinder is greater than the oil pressure in the front chamber, which pushes the piston to complete the opening action; The front chamber of the oil cylinder is connected to the hydraulic main circuit through the opening oil pipe joint, the rear chamber of the oil cylinder is connected to the hydraulic auxiliary circuit through the closing oil pipe joint, and the hydraulic auxiliary circuit is connected to the hydraulic main circuit through a pressure reducing valve; the hydraulic auxiliary circuit includes a rear chamber check valve connected to the closing oil pipe joint and a closing accumulator, and the rear chamber check valve is connected to the closing accumulator and the pressure reducing valve respectively; the hydraulic main circuit includes a flameproof three-phase asynchronous motor, a gear pump, a front chamber check valve connected to the opening oil pipe joint, a disc brake, a flameproof electromagnetic reversing valve, a throttle valve valve, relief valve and secondary relief valve; the flameproof three-phase asynchronous motor is connected to the gear pump, and the flameproof three-phase asynchronous motor is connected to the oil tank through a mesh oil filter; one end of the front chamber check valve is connected to the gear pump, and the other end is respectively connected to the disc brake, the flameproof electromagnetic reversing valve, the accumulator and the pressure reducing valve through a paper oil filter; one end of the relief valve is connected to the oil tank, and the other end is connected to a pressure gauge 1; one end of the throttle valve is connected to the oil tank, and the other end is respectively connected to the flameproof electromagnetic reversing valve and the secondary relief valve, and the secondary relief valve is connected to a pressure gauge 2; The closing oil pipe joint is connected to a first mining pressure sensor; the opening oil pipe joint is connected to a second mining pressure sensor.

2. A high-thrust brake for a belt conveyor according to claim 1, characterized in that: The oil cylinder comprises a cylinder barrel, a cylinder cover connected to the cylinder barrel, a cylinder bottom connected to the cylinder barrel, a piston placed in the cylinder barrel, a piston rod connected to the piston, and a guide sleeve sleeved on the piston rod.

3. A high-thrust brake for a belt conveyor according to claim 2, characterized in that: A nut and an O-type rubber seal ring are provided between the cylinder cover and the cylinder barrel, a guide belt and a Y-shaped ring for a piston rod sealing groove are provided between the cylinder cover and the outer end of the piston rod, an O-type rubber seal ring is provided between the piston rod and the piston, and a piston DAS combined seal ring and a guide ring are provided between the piston and the cylinder barrel.

4. A high-thrust brake for a belt conveyor according to claim 2, characterized in that: The front end of the piston rod is connected to the adjusting rod through a hexagonal thin nut, and the adjusting rod is hinged with an adjusting block.

5. A high-thrust brake for a belt conveyor according to claim 4, characterized in that: The adjusting block and the cylinder bottom are respectively connected to the transmission arm through a pin shaft, and the cylinder pin shaft and the adjusting block pin shaft are both connected with a baffle.

6. A high-thrust brake for a belt conveyor according to claim 1, characterized in that: The upper and lower surfaces of the brake shoe are pressed and fixed by a pressing plate.

7. A high-thrust brake for a belt conveyor according to claim 5, characterized in that: The cylinder bottom is provided with a mounting hole, and a copper sleeve is provided on the mounting hole.

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