WO2018082022A1 - 安全制动控制系统、矿井提升机和安全制动控制方法 - Google Patents

安全制动控制系统、矿井提升机和安全制动控制方法 Download PDF

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Publication number
WO2018082022A1
WO2018082022A1 PCT/CN2016/104638 CN2016104638W WO2018082022A1 WO 2018082022 A1 WO2018082022 A1 WO 2018082022A1 CN 2016104638 W CN2016104638 W CN 2016104638W WO 2018082022 A1 WO2018082022 A1 WO 2018082022A1
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WIPO (PCT)
Prior art keywords
brake
disc
circuit
braking
control
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PCT/CN2016/104638
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English (en)
French (fr)
Inventor
寇子明
吴娟
杨建伟
高贵军
张鹏
张静
秦豪
Original Assignee
太原理工大学
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Application filed by 太原理工大学 filed Critical 太原理工大学
Priority to PCT/CN2016/104638 priority Critical patent/WO2018082022A1/zh
Priority to AU2016428671A priority patent/AU2016428671B2/en
Publication of WO2018082022A1 publication Critical patent/WO2018082022A1/zh

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/24—Operating devices
    • B66D5/26—Operating devices pneumatic or hydraulic
    • B66D5/28—Operating devices pneumatic or hydraulic specially adapted for winding gear, e.g. in mining hoists

Definitions

  • the invention relates to a safety brake control technology, in particular to a safety brake control system and method suitable for an engineering lifting device, and a mine hoist including the safety brake control system.
  • the mine hoist is a working machine in the underground of the mine and on the ground. It can drive the container (cage or bucket) to lift and lower in the wellbore through the wire rope to complete the task of conveying materials and personnel.
  • safe braking is an important requirement for ensuring the safety of materials and personnel.
  • the safe braking methods commonly used in mine hoists are first-class braking, second-level braking and constant deceleration braking.
  • the braking torques of the first-level brake and the second-level brake are determined according to the full-load deflating condition, and the value is not changed after the adjustment.
  • primary and secondary brakes can basically meet the demand.
  • the secondary brakes cause the hoisting machine to decelerate too much, which may cause the wire rope to slip, and may even lead to broken ropes, thus endangering equipment and personal safety.
  • constant deceleration braking can be unaffected by the load, and the deceleration is within a desired range of values during braking. By controlling the deceleration to perform smooth braking, the sliding and disconnection of the wire rope can be avoided. Therefore, the constant deceleration braking system is the preferred safe braking mode for the current coal mine handling emergency.
  • the part of the gate control hardware device is prone to failure.
  • the hydraulic circuit of the disc brake when blocked, it may cause mis-braking or can not be braked at a critical moment to cause a malignant accident.
  • the object of the present invention is to provide a safety brake control system, a mine hoist and a safety brake control method, which can improve the reliability and safety of the engineering lifting equipment when performing safety braking under abnormal working conditions.
  • the present invention provides a safety brake control system for performing safety brake control on an engineering lifting device, including:
  • a disc brake subsystem for safely braking a brake disc of the engineering lifting device by a brake shoe that drives a brake by a hydraulic fluid
  • the electric control subsystem is configured to perform motor braking on the motor of the engineering lifting device when the brake of the disc brake subsystem fails.
  • the disc brake system includes:
  • a disc brake group having at least one set of disc brake brakes for safely braking a brake disc of the engineering lifting device under driving of hydraulic fluid;
  • the switching of the circuit replaces the failed primary brake circuit to provide the corresponding disk brake brake pair with hydraulic fluid that controls the braking torque of the disk brake brake pair.
  • the disc brake subsystem further includes:
  • An electro-hydraulic proportional directional control valve is disposed in the main brake circuit and the backup brake circuit for connecting the main brake circuit and the backup brake circuit to the disc brake group respectively Relationship and flow control;
  • the detecting feedback component includes:
  • a constant decompression control cabinet configured to provide a control signal to the electro-hydraulic proportional reversing valve according to the received sensing signal, so as to implement a constant deceleration braking control of a closed loop control mode of the brake disc of the engineering lifting device;
  • a sensing unit configured to detect a sensing signal capable of characterizing an operating state of the engineering lifting device, and send the obtained sensing signal to the constant pressure reducing control cabinet.
  • the sensing unit comprises at least one of the following sensors:
  • a pressure sensor disposed in each of the main brake circuit and each of the backup brake circuits, It is used for detecting the pressure of the hydraulic pipeline in which it is located, and transmitting the obtained pressure sensing signal to the constant pressure reducing control cabinet;
  • a speed measuring sensor disposed on the reel of the engineering lifting device or the brake disc for detecting the rotation speed of the reel or the brake disc, and transmitting the obtained rotation speed sensing signal to the constant Pressure reducing control cabinet;
  • a gap/stroke sensor disposed in each of the disc brake brakes for detecting a gap/stroke sensing signal of the disc brake brake pair and transmitting the gap/stroke sensing signal to the constant decompression control cabinet .
  • the electric control subsystem is further configured to determine, according to the sensing signal fed back by the detecting feedback component, whether each of the main braking circuits in the disc brake subsystem is ineffective, and if all fail, Then, the motor of the engineering lifting device is braked.
  • the primary brake circuit and the backup brake circuit are each powered by a separate accumulator.
  • the plurality of electro-hydraulic proportional reversing valves are respectively disposed in each of the main brake circuit and the standby brake circuit for controlling the connection relationship between each of the main brake circuits and the backup brake circuit.
  • the switching between the active and standby brake circuits is realized, and the constant deceleration braking control of the brake disc of the engineering lifting device is realized by the flow control of the currently connected brake circuit.
  • an electromagnetic on-off valve group for controlling a communication relationship between the hydraulic fluids is further included in the main brake circuit and the backup brake circuit for controlling the main brake circuit or the backup brake circuit. Turning on and off, and realizing the pressure relief control of the disc brake group.
  • the electromagnetic on-off valve group, the electro-hydraulic proportional reversing valve and the detection feedback component are powered by the standby uninterruptible power supply system under emergency safety braking conditions.
  • the present invention also provides a mine hoist comprising the aforementioned safety brake control system, the mine hoist being the engineering lifting device.
  • the present invention also provides a safety brake control method based on the aforementioned safety brake control system, comprising:
  • the disk brake braking subsystem safely brakes the brake disk of the engineering lifting device by the brake fluid of the hydraulic fluid driving brake;
  • the electric control subsystem sets up the project The motor is ready for motor braking.
  • the disc brake subsystem includes: a disc brake group having at least one set of disc brake brake pairs, and at least one set of main systems respectively connected to each disc brake brake pair in the disc brake brake group And the at least one set of the backup brake circuit; the operation of the brake system of the brake device to brake the brake disk of the engineering lifting device by the hydraulic fluid to drive the brake shoe of the brake comprises:
  • the at least one set of primary brake circuits provides hydraulic fluid for controlling a braking torque of the disk brake brake pair to a corresponding disk brake brake pair of the disk brake brake group such that the corresponding disk brake brake pair is hydraulically Safely braking the brake disc of the engineering lifting device under the driving of the fluid;
  • the at least one set of standby brake circuits replaces the failed main brake circuit by the switching of the hydraulic circuit to the corresponding disk
  • the brake brake pair provides hydraulic fluid that controls the braking torque of the disc brake brake pair.
  • the method further includes: when all the main brake circuits in the disk brake subsystem are failed, the electric control system performs motor braking on the motor of the engineering lifting device.
  • the disc brake subsystem further includes: a detection feedback component, a plurality of electro-hydraulic proportional reversing valves respectively disposed in each of the main brake circuit and the standby brake circuit;
  • the safety brake control method further includes:
  • the electro-hydraulic proportional reversing valve controls the connection relationship between each main brake circuit and the backup brake circuit according to the sensing signal detected by the detection feedback component capable of characterizing the operating state of the engineering lifting device
  • the switching of the active and standby brake circuits and the constant deceleration braking control of the brake disc of the engineering lifting device are realized by the flow control of the currently connected brake circuit.
  • the present invention provides two sets of brake subsystems, namely, a disk brake brake subsystem and an electric control dynamic subsystem, for the engineering lifting device, and can start the electric control movement in time under the abnormal condition of the mechanical brake control failure.
  • a disk brake brake subsystem and an electric control dynamic subsystem for the engineering lifting device, and can start the electric control movement in time under the abnormal condition of the mechanical brake control failure.
  • the disc brake subsystem and the electric control subsystem can realize independent emergency protection, and can also realize mutual protection and realize electromechanical blocking, thereby improving the safety braking of the engineering lifting equipment under abnormal working conditions. Reliability and security.
  • FIG. 1 is a schematic diagram of the principle of an embodiment of a safety brake control system of the present invention.
  • FIG. 2 is a schematic diagram of the principle of another embodiment of the safety brake control system of the present invention.
  • FIG. 3 is a schematic diagram of the principle of still another embodiment of the safety brake control system of the present invention.
  • FIG. 4 is a schematic structural view of an embodiment of a safety brake control system applied to a mine hoist according to the present invention.
  • FIG. 5 is a schematic diagram showing the principle of hydraulic control of the disc brake subsystem in the embodiment of the safety brake control system of the present invention.
  • FIG. 1 is a schematic diagram showing the principle of an embodiment of the safety brake control system of the present invention.
  • the safety brake control system is used to perform safety brake control on the engineering lifting equipment.
  • the structure of the mine hoist is applied in conjunction with the embodiment of the safety brake control system shown in FIG. 4.
  • the safety brake control system includes: a brake brake subsystem 100 and an electric control subsystem 200.
  • the disc brake system 100 is used for safely braking the brake disc 3 of the engineering lifting device by a brake shoe that drives the brake by hydraulic fluid.
  • the electric control subsystem 200 is configured to perform motor braking on the motor 5 of the engineering lifting device when the brake of the disk brake subsystem 100 fails.
  • the safety brake control system is provided with two sets of brake subsystems, the brake system and the electric control subsystem, for the engineering lifting device, which can be started in an abnormal situation in which the mechanical brake control fails.
  • the electric control moves to ensure the safe braking effect of the engineering lifting equipment and avoid the occurrence of malignant accidents.
  • the disc brake subsystem and the electric control subsystem can realize independent emergency protection, and can also realize mutual protection and realize electromechanical blocking, thereby improving the safety braking of the engineering lifting equipment under abnormal working conditions. Reliability and security.
  • the disc brake system 100 is braked by a disc brake, and the brake shoe of the disc brake is driven by hydraulic fluid (for example, hydraulic oil or the like), and the reel 1 of the engineering lifting device rotates synchronously with the brake disc 3, and passes through the brake The tile presses the brake disc 3 to obtain a large frictional force, thereby achieving the deceleration and stop of the reel 1.
  • the disc brake system 100 can adopt a control scheme of electro-hydraulic closed-loop control to achieve constant deceleration control under emergency braking conditions.
  • the disc brake subsystem 100 may specifically include a disc brake set 110, at least one set of primary brake circuits 120, and at least one set of alternate brake circuits 130.
  • the disc brake brake group 110 has at least one set of disc brake brake pairs 2 for safely braking the brake disc 3 of the engineering lifting device under the driving of hydraulic fluid.
  • At least one set of primary brake circuits 120 are coupled to respective disk brake brake pairs 2 of the disk brake brake group 110 for use in the disk brake brake group 110 when the engineering lift device requires emergency braking
  • the corresponding disc brake brake pair 2 provides hydraulic fluid that controls the braking torque of the disc brake brake pair 2.
  • At least one set of alternate brake circuits 130 are coupled to respective disk brake brake pairs 2 of the disk brake brake group 110 for failure of at least a portion of the primary brake circuit 120 in the primary brake circuit 120 At the same time, the hydraulic circuit that controls the braking torque of the disk brake brake pair 2 is supplied to the corresponding disk brake brake pair 2 by switching the hydraulic circuit instead of the failed primary brake circuit 120.
  • the main brake circuit 120 can be used as the brake brake in the normal state and in the emergency braking condition. When one or several main brake circuits 120 fail, the corresponding backup brake circuit can be utilized. 130 switches to continue to provide the disc brake function. Moreover, for the disc brake system 100, the disc brake brake pair 2, the main brake circuit 120 and the backup brake circuit 130 can be set to N groups, regardless of the normal operation or the parking brake condition, the N group disc The probability of simultaneous failure of the brake brake pair 2 is very small. Even if one or several main brake circuits 120 fail, it can be conveniently switched to supply hydraulic fluid to the corresponding brake disc brake pair 2 by the backup brake circuit 130. This process is very fast and has less impact on the production time of the engineering lifting equipment.
  • the N sets of disc brake brake pair 2 and the corresponding main backup brake circuit plus the motor brake function realized by the aforementioned electric control mover subsystem 200 form an N+1 electromechanical lockout scheme, which can be very Effectively reduce or avoid the vicious accident caused by mis-braking or unable to brake at the critical time, greatly improving the reliability and safety of the engineering lifting equipment during safe braking under abnormal conditions.
  • the disc brake subsystem 100 may further include: an electro-hydraulic proportional reversing valve 140 and a detection feedback component 150.
  • the electro-hydraulic proportional reversing valve 140 is disposed in the main brake circuit 120
  • the standby brake circuit 130 is configured to control the communication relationship and the flow rate of the main brake circuit 120 and the backup brake circuit 130 with the disk brake group 110, respectively.
  • the detection feedback component 150 is configured to detect a sensing signal capable of characterizing an operational state of the engineering lifting device and feed back to the electro-hydraulic proportional reversing valve 140 and the electrically controlled moving subsystem 200.
  • the electro-hydraulic proportional directional control valve 140 can perform the opening and closing of the brake circuit and the flow rate of the brake circuit in which it is provided by the detection feedback component 150, thereby implementing the brake control of the constant deceleration of the disc brake.
  • the detection feedback component 150 can detect the sensing signals (such as the rotational speed of the reel, the hydraulic pressure of the brake circuit, the gap of the brake disc brake, the stroke, etc.) that characterize the operating state of the engineering lifting device, and the detected signals are detected.
  • the sensing signal is also required to be supplied to the electric control subsystem 200, so that the electric control subsystem 200 can be used in time to improve the project when the disc brake subsystem fails.
  • the motor 5 of the device brakes the motor.
  • the brake strategy of the disc brake and the electric control is preferably a disc brake, and the electric control is started only when all the disc brakes fail.
  • the electric control subsystem 200 can determine, according to the sensing signal fed back by the detection feedback component 150, whether each of the main brake circuits 120 in the disk brake subsystem 100 is ineffective, and if all fails, the device The motor 5 of the engineering lifting device performs motor braking.
  • the source of hydraulic fluid for the primary brake circuit 120 and the backup brake circuit 130 may be a pump driven by a motor or an accumulator. Considering that the emergency braking condition may be accompanied by a power failure, it is preferred that the primary brake circuit 120 and the backup brake circuit 130 are each powered by a separate accumulator so that the pump cannot be driven even after the motor is de-energized.
  • the main brake circuit 120 and the backup brake circuit provide hydraulic fluid, and the accumulator can also be used to complete the supply of hydraulic fluid for braking.
  • a plurality of electro-hydraulic proportional directional valves 140 can be employed accordingly.
  • electro-hydraulic proportional reversing valves 140 By providing separate electro-hydraulic proportional reversing valves 140 in each of the main brake circuit 120 and the backup brake circuit 130, the connection relationship between each of the main brake circuit 120 and the backup brake circuit 130 can be conveniently controlled.
  • To realize the switching of the main and auxiliary brake circuits, and realize the constant deceleration braking control of the brake disc 3 of the engineering lifting device by the flow control of the currently connected brake circuit, thereby simplifying the electro-hydraulic proportional reversing valve The design of the valve body structure and control logic.
  • a connection relationship for controlling the hydraulic fluid may be further added to the main brake circuit 120 and the backup brake circuit 130.
  • the electromagnetic on-off valve group controls the on-off of the main brake circuit 120 or the backup brake circuit 130 through the electromagnetic on-off valve group, and realizes the pressure relief control of the disc brake group 110.
  • the electromagnetic on-off valve group, the electro-hydraulic proportional reversing valve 140 and the detection feedback component 150 are preferably powered by the standby uninterrupted power under the emergency safety braking condition ( The UPS) system supplies power to ensure that the safe braking of the disc brake subsystem is smooth.
  • the UPS emergency safety braking condition
  • FIG. 3 is a schematic diagram showing the principle of still another embodiment of the safety brake control system of the present invention.
  • the detection feedback component 150 in this embodiment specifically includes a constant pressure reduction control cabinet 151 and a sensing unit 152.
  • the constant pressure reducing control cabinet 151 is configured to provide a control signal to the electro-hydraulic proportional reversing valve 140 according to the received sensing signal, so as to achieve a constant deceleration of the closed loop control mode of the brake disc 3 of the engineering lifting device.
  • the sensing unit 152 is configured to detect a sensing signal capable of characterizing an operating state of the engineering lifting device, and send the obtained sensing signal to the constant pressure reducing control cabinet 151.
  • the sensing unit 152 may include one or more of the following sensors, such as a pressure sensor, a speed sensor 7, and a gap/stroke sensor.
  • a pressure sensor may be disposed in each of the main brake circuit 120 and each of the backup brake circuits 130 for detecting the pressure of the hydraulic circuit in which it is located, and transmitting the obtained pressure sensing signal to the constant Decompression control cabinet 151.
  • a speed measuring sensor 7 is shown in Fig. 4, which is arranged on the reel 1 or the brake disc 3 of the engineering lifting device for detecting the rotational speed of the reel 1 or the brake disc 3, and The obtained rotational speed sensing signal is sent to the constant pressure reducing control cabinet 151.
  • a gap/stroke sensor is disposed in each of the disc brake brake pairs 2 for detecting a gap/stroke sensing signal of the disc brake brake pair 2, and transmitting the gap/stroke sensing signal to the constant decompression control Cabinet 151.
  • the foregoing embodiments of the safety brake control system of the present invention are applicable to various engineering lifting devices, and are particularly suitable for a mine hoist, which can effectively improve the safety performance of a mine hoist, that is, the present invention also provides a mine hoist
  • the foregoing embodiment of the safety brake control system is included, and the mine hoist is the engineering lifting device described in the embodiment of the safety brake control system.
  • the present invention also provides a corresponding safety brake control method, including: when the engineering lift device is in emergency safety braking, the brake cylinder brake system 100 drives the brake shoe pair by hydraulic fluid The brake disc 3 of the engineering lifting device performs safety braking; when the braking of the disc brake subsystem 100 fails, the electric control subsystem 200 performs the motor 5 of the engineering lifting device. Motor brake.
  • the disk brake brake subsystem 100 specifically includes: a disk brake brake group 110 having at least one set of disk brake brake pairs 2, and at least one group of masters respectively connected to respective disk brake brake pairs 2 of the disk brake brake group 110
  • the disk brake system 100 can safely brake the brake disk 3 of the engineering lifting device by the brake fluid of the hydraulic fluid driving brake.
  • the at least one set of primary brake circuit 120 provides hydraulic fluid for controlling the braking torque of the disk brake brake pair 2 to the corresponding disk brake brake pair 2 of the disk brake group 110 to make the corresponding disk brake
  • the brake pair 2 is safely braked by the hydraulic fluid to brake the brake disc 3 of the engineering lifting device;
  • the at least one set of backup brake circuits 130 replaces the failed primary brake circuit 120 by switching of the hydraulic circuit.
  • a hydraulic fluid that controls the braking torque of the disc brake brake pair 2 is supplied to the corresponding disc brake brake pair 2.
  • the motor 5 of the engineering lifting device can be braked by the electric control system 200.
  • the disk brake subsystem 100 may further include: a detection feedback component 150, a plurality of electro-hydraulic ratios respectively disposed in each of the main brake circuit 120 and the backup brake circuit 130
  • the reversing valve 140 correspondingly, the safety brake control method may further include:
  • the electro-hydraulic proportional directional control valve controls the communication between each of the main brake circuit 120 and the backup brake circuit 130 according to the sensing signal detected by the detection feedback component 150 that can characterize the operating state of the engineering hoisting device.
  • the relationship is to realize the switching of the active and standby brake circuits, and the constant deceleration braking control of the brake disc 3 of the engineering lifting device is realized by the flow control of the currently connected brake circuit.
  • the motor 5 supplies a driving force to the reel 1 through a speed reducer 8
  • a brake disc 3 is fixedly mounted on the reel 1
  • a plurality of disc brake brake pairs 2 are disposed on both sides of the brake disc 3
  • the cylinder of the disc brake brake pair 2 communicates with the oil source for braking via the hydraulic circuit 4.
  • the hydraulic circuit 4 connected to the disc brake brake pair 2 includes a plurality of sets of main and standby brake circuits, which are switched
  • the main standby brake circuit can be switched to the corresponding standby brake circuit in time when some of the main brake circuits fail, to ensure the braking effect of the disc brake brake pair 2.
  • the main brake circuit returns to normal, it is switched back to the corresponding main brake circuit to restore its supply of hydraulic fluid to the brake disc brake pair 2.
  • a speed measuring sensor 7 is disposed at an outer peripheral position of the brake disc 3, and the speed signal of the brake disc 3 measured by the speed measuring sensor 7 is sent to the electronic control device 6, and the electronic control device 6 can determine whether the disc brake brake pair 2 is based on the rotational speed signal. All have failed, for example, whether or not the brake brake pair 2 does not achieve the braking effect based on the current rotational speed. If it is determined that all of the disc brake brake pairs 2 have failed, the electronic control device 6 can send a control signal to the motor 5 to control the rotational speed of the reel 1 by the motor 5 to achieve the braking action.
  • Figure 5 shows an example of a related hydraulic control of a hydraulic circuit in communication with a disc brake brake pair.
  • a disc brake brake pair For convenience of description, only two sets of disc brake brake pairs are schematically illustrated in Fig. 5, which are disc brake brake pairs 9.1 and 9.2, respectively.
  • the rod chambers of the cylinder brake pair 9.1 and 9.2 are in communication with each other, and are connected to the electro-hydraulic proportional valve 6.1, 6.2 via a plurality of electromagnetic on-off valves 8.1, 8.2, and to the electro-pneumatic on-off valves 8.3, 8.4. tank.
  • the electro-hydraulic proportional directional valves 6.1 and 6.2 are in communication with the accumulators 7.1 and 7.2, respectively, and are in communication with the oil pumps 2.1 and 2.2.
  • the constant deceleration braking process can be achieved either by supplying the pressure oil to the disc brake brake pair via the oil pumps 2.1 and 2.2, or by providing the pressure oil to the disc brake brake pair by the accumulator 7.1 or 7.2.
  • the electromagnetic on-off valve 8.3 when the electromagnetic on-off valve 8.3 is energized, the communication relationship between the disc brake brake pairs 9.1 and 9.2 and the fuel tank is cut off, and at this time, by controlling the signal voltage 10V to the control electro-hydraulic proportional reversing valve 6.1, The electro-hydraulic proportional directional valve 6.1 operates in the left position.
  • the pressure oil pumped by the oil pump 2.1 enters the electro-hydraulic proportional reversing valve 6.1 via the one-way valve 5.1 and the one-way valve 5.3, and the pressure oil flows out from the electro-hydraulic proportional reversing valve 6.1, and then is branched to the electromagnetic on-off valves 8.1 and 8.2, Then, after joining, press the disc brake brake pair 9.1 and 9.2 to realize the braking effect of the disc brake brake pair on the brake disc. At the same time, the pressure oil will also flow to the accumulators 7.1 and 7.2 via the one-way valves 5.3 and 5.4 for pressure storage.
  • the relief valves 4.1 and 4.2 provide maximum system pressure regulation for the oil pumps 2.1 and 2.2, while the relief valves 4.3 and 4.4 provide maximum storage pressure protection for the accumulators 7.1 and 7.2, respectively.
  • the electro-hydraulic proportional reversing valves 6.1 and 6.2 are respectively connected to the accumulators 7.1 and 7.2, that is, the electro-hydraulic proportional reversing valve 6.1 can receive the pressure oil from the accumulator 7.1 for supply to the disc brake brake pair, this supply
  • the hydraulic circuit for the brake disc brake pair can be used as the main brake circuit.
  • the energy storage can be realized by the switching operation of the electro-hydraulic proportional reversing valves 6.1 and 6.2.
  • the 7.2 supplies the pressure oil to the disc brake brake pairs 9.1 and 9.2 via the electro-hydraulic proportional reversing valve 6.2, ie the spare brake circuit acts as a brake instead of the main brake circuit.
  • the entire door of the coal mine is powered off, and emergency safety braking is required immediately.
  • the electric energy required for the action of the electromagnetic on-off valve and the electro-hydraulic proportional reversing valve can be provided by the standby UPS, and the pressure required for the disc brake pair can be provided by the accumulator.
  • the electromagnetic on-off valve 8.3 is energized, and the control signal of the electro-hydraulic proportional reversing valve 6.1 is adjusted at -10V to 10V, and the pressure oil in the accumulator 7.1 directly enters the electro-hydraulic proportional reversing valve 6.1.
  • the liquid proportional reversing valve 6.1 changes the flow rate between -10V and 10V to change the flow rate, and then adjusts the pressure of the pressure oil after passing through the electro-hydraulic proportional reversing valve.
  • the pressure oil after adjusting the pressure enters the electromagnetic flux respectively.
  • Valves 8.1 and 8.2 are broken and rejoined together into the brake disc brakes 9.1 and 9.2.
  • the oil pressure entering the disc brake brake pair can be changed, and the pressure applied to the brake disc can be controlled by the oil pressure to adjust the frictional force of the brake disc to the brake disc.
  • the size, and thus the braking torque, is adjusted to achieve constant deceleration braking of the engineering lifting equipment.
  • the backup brake circuit needs to be activated to replace the failed main brake circuit. Achieve constant deceleration braking.
  • the electrical energy required to operate the electromagnetic on-off valve and the electro-hydraulic proportional diverter valve in the alternate brake circuit can also be provided by the backup UPS, and the pressure required by the brake disc brake pair can be provided by the accumulator.
  • the electro-hydraulic proportional reversing valve 6.1 can be closed, and the solenoid valves 8.1, 8.2 and 8.3 are energized, and the control signal of the electro-hydraulic proportional reversing valve 6.2 is adjusted from -10V to 10V, in the accumulator 7.2
  • the pressure oil directly enters the electro-hydraulic proportional reversing valve 6.2.
  • the electro-hydraulic proportional reversing valve 6.2 changes the control signal between -10V and 10V to change the flow rate, and then adjusts the electro-hydraulic ratio.
  • the pressure of the pressure oil behind the valve, the pressure oil after adjusting the pressure enters the electromagnetic on-off valves 8.1 and 8.2, respectively, and then merges into the disc brake brake pairs 9.1 and 9.2.

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Abstract

公开了一种安全制动控制系统、矿井提升机和安全制动控制方法。该安全制动控制系统用于对工程提升设备进行安全制动控制，包括：盘闸制动子系统(100)，用于通过液压流体驱动制动器的闸瓦对工程提升设备的制动盘(3)进行安全制动；电控制动子系统(200)，用于在盘闸制动子系统(100)的制动失效时对工程提升设备的电机(5)进行电机制动。由于针对于工程提升设备设置了盘闸制动子系统和电控制动子系统两套制动子系统，能够在机械闸控失效的异常情况下及时启动电控制动来确保工程提升设备的安全制动作用，避免恶性事故的发生，改善工程提升设备在异常工况下进行安全制动时的可靠性和安全性。

Description

安全制动控制系统、矿井提升机和安全制动控制方法 技术领域
本发明涉及安全制动控制技术，尤其涉及一种适用于工程提升设备的安全制动控制系统和方法，以及包括了该安全制动控制系统的矿井提升机。
背景技术
矿井提升机是一种是在矿井井下和地面的工作机械，能够通过钢丝绳带动容器(罐笼或箕斗)在井筒中升降，完成输送物料和人员的任务。对于矿井提升机来说，安全制动是确保物料和人员输送安全的重要要求。
在目前矿井提升机所常用的安全制动方式有一级制动、二级制动和恒减速制动。一级制动和二级制动的制动力矩均是按照全载下放工况来确定，其数值调整后就不再改变。对于提升载荷变化小的矿井，一级制动和二级制动基本能够满足需求。而对于提升载荷变化较大和提升速度较高的矿井，二级制动使得提升机运行减速度变化过大，容易造成钢丝绳滑动，甚至可能导致断绳现象，从而危及到设备及人身安全。相比之下，恒减速制动能够不受载荷影响，在制动过程中减速度在一个预期的数值范围内。通过控制减速度来进行平稳制动，可以避免钢丝绳的滑动和断开，因此恒减速制动系统是目前煤矿处理紧急事件的优选安全制动方式。
在目前已有的恒减速制动系统中，闸控硬件设备部分容易发生故障，例如盘式制动器液压回路发生堵塞时，可能会造成误制动或关键时刻无法制动而引起恶性事故。
发明内容
本发明的目的是提出一种安全制动控制系统、矿井提升机和安全制动控制方法，能够改善工程提升设备在异常工况下进行安全制动时的可靠性和安全性。
为实现上述目的，本发明提供了一种安全制动控制系统，用于对工程提升设备进行安全制动控制，包括：
盘闸制动子系统，用于通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘进行安全制动；
电控制动子系统，用于在所述盘闸制动子系统的制动失效时对所述工程提升设备的电机进行电机制动。
进一步的，所述盘闸制动子系统包括：
盘闸制动器组，具有至少一组盘闸制动器副，用于在液压流体的驱动下对所述工程提升设备的制动盘进行安全制动；
至少一组主用制动回路，分别与所述盘闸制动器组中的各个盘闸制动器副连接，用于在所述工程提升设备需要紧急制动时，向所述盘闸制动器组中对应的盘闸制动器副提供控制所述盘闸制动器副的制动力矩的液压流体；
至少一组备用制动回路，分别与所述盘闸制动器组中的各个盘闸制动器副连接，用于在所述主用制动回路中的至少部分主用制动回路发生故障时，通过液压回路的切换来替代发生故障的主用制动回路来向对应的盘闸制动器副提供控制所述盘闸制动器副的制动力矩的液压流体。
进一步的，所述盘闸制动子系统还包括：
电液比例换向阀，设置在所述主用制动回路和所述备用制动回路中，用于对所述主用制动回路和所述备用制动回路分别与盘闸制动器组的连通关系和流量进行控制；
检测反馈部件，用于检测能够表征所述工程提升设备的运行状态的传感信号，并反馈给所述电液比例换向阀和所述电控制动子系统。
进一步的，所述检测反馈部件包括：
恒减压控制柜，用于根据接收到的传感信号向所述电液比例换向阀提供控制信号，以便对所述工程提升设备的制动盘实现闭环控制方式的恒减速制动控制；
传感单元，用于检测能够表征所述工程提升设备的运行状态的传感信号，并将获得的传感信号发送给所述恒减压控制柜。
进一步的，所述传感单元包括以下至少一种传感器：
压力传感器，设置在各个所述主用制动回路和各个所述备用制动回路中， 用于检测所在液压管路的压力，并将获得的压力传感信号发送给所述恒减压控制柜；
测速传感器，设置在所述工程提升设备的卷筒或所述制动盘上，用于检测所述卷筒或所述制动盘的转速，并将获得的转速传感信号发送给所述恒减压控制柜；
间隙/行程传感器，设置在各个盘闸制动器副中，用于检测所述盘闸制动器副的间隙/行程传感信号，并将所述间隙/行程传感信号发送给所述恒减压控制柜。
进一步的，所述电控制动子系统还用于根据所述检测反馈部件反馈的传感信号判断所述盘闸制动子系统中的各个主用制动回路是否全部失效，如果全部失效，则对所述工程提升设备的电机进行电机制动。
进一步的，所述主用制动回路和备用制动回路各自由独立的蓄能器供能。
进一步的，所述电液比例换向阀为多个，分别设置在各个主用制动回路和备用制动回路中，用于通过控制每个主用制动回路和备用制动回路的连通关系来实现主备制动回路的切换，并通过对当前连通的制动回路的流量控制来实现对所述工程提升设备的制动盘的恒减速制动控制。
进一步的，在所述主用制动回路和所述备用制动回路中还包括控制液压流体的连通关系的电磁通断阀组，用于控制所述主用制动回路或备用制动回路的通断，并实现所述盘闸制动器组的卸压控制。
进一步的，所述电磁通断阀组、电液比例换向阀和检测反馈部件在紧急安全制动状况下由备用不间断供电系统供电。
为实现上述目的，本发明还提供了一种矿井提升机，包括前述的安全制动控制系统，所述矿井提升机为所述工程提升设备。
为实现上述目的，本发明还提供了一种基于前述的安全制动控制系统的安全制动控制方法，包括：
在工程提升设备紧急安全制动时，盘闸制动子系统通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘进行安全制动；
当所述盘闸制动子系统的制动失效时，电控制动子系统对所述工程提升设 备的电机进行电机制动。
进一步的，所述盘闸制动子系统包括：具有至少一组盘闸制动器副的盘闸制动器组、分别与所述盘闸制动器组中的各个盘闸制动器副连接的至少一组主用制动回路和至少一组备用制动回路；所述盘闸制动子系统通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘进行安全制动的操作具体包括：
所述至少一组主用制动回路向所述盘闸制动器组中对应的盘闸制动器副提供控制所述盘闸制动器副的制动力矩的液压流体，以使对应的盘闸制动器副在液压流体的驱动下对所述工程提升设备的制动盘进行安全制动；
在所述主用制动回路中的至少部分主用制动回路发生故障时，所述至少一组备用制动回路通过液压回路的切换来替代发生故障的主用制动回路来向对应的盘闸制动器副提供控制所述盘闸制动器副的制动力矩的液压流体。
进一步的，还包括：当所述盘闸制动子系统中的各个主用制动回路全部失效时，所述电控制动子系统对所述工程提升设备的电机进行电机制动。
进一步的，所述盘闸制动子系统还包括：检测反馈部件、分别设置在各个主用制动回路和备用制动回路中的多个电液比例换向阀；
所述安全制动控制方法还包括：
所述电液比例换向阀根据所述检测反馈部件检测到的能够表征所述工程提升设备的运行状态的传感信号，控制每个主用制动回路和备用制动回路的连通关系来实现主备制动回路的切换，并通过对当前连通的制动回路的流量控制来实现对所述工程提升设备的制动盘的恒减速制动控制。
基于上述技术方案，本发明针对于工程提升设备设置了盘闸制动子系统和电控制动子系统两套制动子系统，能够在机械闸控失效的异常情况下及时启动电控制动来确保工程提升设备的安全制动作用，避免恶性事故的发生。此外，盘闸制动子系统和电控制动子系统可以实现独立的应急保护，也可以实现相互之间的保护，实现机电闭锁，进而改善工程提升设备在异常工况下进行安全制动时的可靠性和安全性。
附图说明
此处所说明的附图用来提供对本发明的进一步理解，构成本申请的一部分，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1为本发明安全制动控制系统的一实施例的原理示意图。
图2为本发明安全制动控制系统的另一实施例的原理示意图。
图3为本发明安全制动控制系统的又一实施例的原理示意图。
图4为本发明安全制动控制系统实施例应用在矿井提升机的结构示意图。
图5为本发明安全制动控制系统实施例中盘闸制动子系统的液压控制实例的原理示意图。
具体实施方式
下面通过附图和实施例，对本发明的技术方案做进一步的详细描述。
如图1所示，为本发明安全制动控制系统的一实施例的原理示意图。在本实施例中，安全制动控制系统用于对工程提升设备进行安全制动控制。结合图4所示的安全制动控制系统实施例应用在矿井提升机的结构示意图，安全制动控制系统包括：盘闸制动子系统100和电控制动子系统200。其中，盘闸制动子系统100用于通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘3进行安全制动。电控制动子系统200用于在所述盘闸制动子系统100的制动失效时对所述工程提升设备的电机5进行电机制动。
在本实施例中，安全制动控制系统针对于工程提升设备设置了盘闸制动子系统和电控制动子系统两套制动子系统，能够在机械闸控失效的异常情况下及时启动电控制动来确保工程提升设备的安全制动作用，避免恶性事故的发生。此外，盘闸制动子系统和电控制动子系统可以实现独立的应急保护，也可以实现相互之间的保护，实现机电闭锁，进而改善工程提升设备在异常工况下进行安全制动时的可靠性和安全性。
盘闸制动子系统100采用盘形制动器进行制动，利用液压流体(例如液压油等)驱动盘形制动器的闸瓦，而工程提升设备的卷筒1与制动盘3同步转动，通过闸瓦挤紧制动盘3来获得较大的摩擦力，进而实现卷筒1的减速和停止。在 本实施例中，盘闸制动子系统100可采用电液闭环控制的控制方案，以实现紧急制动工况下的恒减速控制。
如图2所示，为本发明安全制动控制系统的另一实施例的原理示意图。与上一实施例相比，所述盘闸制动子系统100可具体包括：盘闸制动器组110、至少一组主用制动回路120和至少一组备用制动回路130。其中，盘闸制动器组110具有至少一组盘闸制动器副2，用于在液压流体的驱动下对所述工程提升设备的制动盘3进行安全制动。
至少一组主用制动回路120分别与所述盘闸制动器组110中的各个盘闸制动器副2连接，用于在所述工程提升设备需要紧急制动时，向所述盘闸制动器组110中对应的盘闸制动器副2提供控制所述盘闸制动器副2的制动力矩的液压流体。至少一组备用制动回路130分别与所述盘闸制动器组110中的各个盘闸制动器副2连接，用于在所述主用制动回路120中的至少部分主用制动回路120发生故障时，通过液压回路的切换来替代发生故障的主用制动回路120来向对应的盘闸制动器副2提供控制所述盘闸制动器副2的制动力矩的液压流体。
这里的主用制动回路120可作为正常状态下和紧急制动情况下的盘闸制动，当某条或某几条主用制动回路120发生故障时，可以利用对应的备用制动回路130进行切换，进而继续提供盘闸制动功能。而且对于盘闸制动子系统100来说，盘闸制动器副2、主用制动回路120和备用制动回路130可以设置为N组，无论在正常运行还是停车制动工况，N组盘闸制动器副2同时失效的概率非常小，即使有一条或几条主用制动回路120发生故障，也可以方便的切换成由备用制动回路130给对应的盘闸制动器副2提供液压流体，这个过程非常快捷，对工程提升设备的生产时间影响较少。
这里的N组盘闸制动器副2和对应的主备用制动回路加上前面提到的电控制动子系统200所实现的电机制动功能，形成了N+1的机电闭锁方案，能够非常有效的减少或避免因误制动或关键时候无法制动所引起的恶性事故，极大地改善工程提升设备在异常工况下进行安全制动时的可靠性和安全性。
在图2中，盘闸制动子系统100还可以进一步包括：电液比例换向阀140和检测反馈部件150。其中，电液比例换向阀140设置在所述主用制动回路120 和所述备用制动回路130中，用于对所述主用制动回路120和所述备用制动回路130分别与盘闸制动器组110的连通关系和流量进行控制。检测反馈部件150用于检测能够表征所述工程提升设备的运行状态的传感信号，并反馈给所述电液比例换向阀140和所述电控制动子系统200。
电液比例换向阀140可以由检测反馈部件150提供的电控信号执行其所在制动回路的开闭以及流量，进而实现盘形制动器的恒定减速度的制动控制。检测反馈部件150可以对表征工程提升设备的运行状态的传感信号(例如卷筒的转速、制动回路的油压、盘闸制动器副的间隙、行程等传感信号)进行检测，检测到的传感信号除了提供给电液比例换向阀140，也需要提供给电控制动子系统200，以便在盘闸制动子系统失效时能够及时地利用电控制动子系统200对工程提升设备的电机5进行电机制动。
盘闸制动和电控制动的制动策略优选采用盘闸制动，只在盘闸制动全部失效时启动电控制动。电控制动子系统200可以根据所述检测反馈部件150反馈的传感信号判断所述盘闸制动子系统100中的各个主用制动回路120是否全部失效，如果全部失效，则对所述工程提升设备的电机5进行电机制动。
主用制动回路120和备用制动回路130的液压流体来源可以是由电机驱动的泵，也可以是蓄能器。考虑到紧急制动工况可能伴随的是断电，因此优选使主用制动回路120和备用制动回路130各自由独立的蓄能器供能，这样即便电机断电后无法驱动泵来向主用制动回路120和备用制动回路提供液压流体，也能够利用蓄能器来完成制动用的液压流体的供应。
考虑到主用制动回路120和备用制动回路130可以设置多个，那么相应的可以采用多个电液比例换向阀140。通过在每个主用制动回路120和备用制动回路130中分别设置独立的电液比例换向阀140，能够方便的控制每个主用制动回路120和备用制动回路130的连通关系来实现主备制动回路的切换，并通过对当前连通的制动回路的流量控制来实现对所述工程提升设备的制动盘3的恒减速制动控制，进而简化电液比例换向阀的阀体结构和控制逻辑的设计。
为了正常工作制动的需要以及增加主备制动回路的控制功能，还可以在主用制动回路120和所述备用制动回路130中进一步加入控制液压流体的连通关系 的电磁通断阀组，通过电磁通断阀组来控制所述主用制动回路120或备用制动回路130的通断，并实现所述盘闸制动器组110的卸压控制。相应的，为了避免紧急安全制动状况下可能伴随的断电情况，电磁通断阀组、电液比例换向阀140和检测反馈部件150优选在紧急安全制动状况下由备用不间断供电(UPS)系统供电，从而确保盘闸制动子系统的安全制动顺利进行。
如图3所示，为本发明安全制动控制系统的又一实施例的原理示意图。与上一实施例相比，本实施例中的检测反馈部件150具体包括：恒减压控制柜151和传感单元152。其中，恒减压控制柜151用于根据接收到的传感信号向所述电液比例换向阀140提供控制信号，以便对所述工程提升设备的制动盘3实现闭环控制方式的恒减速制动控制。传感单元152用于检测能够表征所述工程提升设备的运行状态的传感信号，并将获得的传感信号发送给所述恒减压控制柜151。
传感单元152可以包括以下一种或多种传感器，例如压力传感器、测速传感器7和间隙/行程传感器等。其中，压力传感器可以设置在各个所述主用制动回路120和各个所述备用制动回路130中，用于检测所在液压管路的压力，并将获得的压力传感信号发送给所述恒减压控制柜151。图4中示出了测速传感器7，该测速传感器7设置在所述工程提升设备的卷筒1或制动盘3上，用于检测所述卷筒1或制动盘3的转速，并将获得的转速传感信号发送给所述恒减压控制柜151。间隙/行程传感器设置在各个盘闸制动器副2中，用于检测所述盘闸制动器副2的间隙/行程传感信号，并将所述间隙/行程传感信号发送给所述恒减压控制柜151。
上述本发明安全制动控制系统的各个实施例可适用于各种工程提升设备，尤其适用于矿井提升机，能够有效地提高矿井提升机的安全性能，即本发明还提供了一种矿井提升机，包括前述的安全制动控制系统实施例，而该矿井提升机即为安全制动控制系统实施例中所描述的工程提升设备。
基于前述的安全制动控制系统，本发明还提供了对应的安全制动控制方法，包括：在工程提升设备紧急安全制动时，盘闸制动子系统100通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘3进行安全制动；当所述盘闸制动子系统100的制动失效时，电控制动子系统200对所述工程提升设备的电机5进行 电机制动。
当盘闸制动子系统100具体包括：具有至少一组盘闸制动器副2的盘闸制动器组110、分别与所述盘闸制动器组110中的各个盘闸制动器副2连接的至少一组主用制动回路120和至少一组备用制动回路130时，盘闸制动子系统100通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘3进行安全制动的操作可以具体包括：
所述至少一组主用制动回路120向所述盘闸制动器组110中对应的盘闸制动器副2提供控制所述盘闸制动器副2的制动力矩的液压流体，以使对应的盘闸制动器副2在液压流体的驱动下对所述工程提升设备的制动盘3进行安全制动；
在所述主用制动回路120中的至少部分主用制动回路120发生故障时，所述至少一组备用制动回路130通过液压回路的切换来替代发生故障的主用制动回路120来向对应的盘闸制动器副2提供控制所述盘闸制动器副2的制动力矩的液压流体。
而当所述盘闸制动子系统100中的各个主用制动回路120全部失效时，可由所述电控制动子系统200对所述工程提升设备的电机5进行电机制动。
在另一个控制方法实施例中，所述盘闸制动子系统100还可以包括：检测反馈部件150、分别设置在各个主用制动回路120和备用制动回路130中的多个电液比例换向阀140；相应的，所述安全制动控制方法可以进一步包括：
所述电液比例换向阀根据所述检测反馈部件150检测到的能够表征所述工程提升设备的运行状态的传感信号，控制每个主用制动回路120和备用制动回路130的连通关系来实现主备制动回路的切换，并通过对当前连通的制动回路的流量控制来实现对所述工程提升设备的制动盘3的恒减速制动控制。
前面对本发明安全制动控制系统及安全制动控制方法的各个实施例进行了说明。下面将结合图4所示的本发明安全制动控制系统实施例应用在矿井提升机的结构进一步对本发明进行说明。在图4中，电机5通过减速器8向卷筒1提供驱动力，卷筒1上固定安装有制动盘3，在制动盘3的两侧上可设置多个盘闸制动器副2，盘闸制动器副2的油缸通过液压回路4与制动用的油源连通。这些盘闸制动器副2所连接的液压回路4包括了多组主用和备用的制动回路，通过切换 主备用的制动回路可以在部分主用制动回路发生故障时及时切换成对应的备用制动回路，以确保盘闸制动器副2的制动作用。当主用制动回路恢复正常时，再切换回对应的主用制动回路，以恢复其对盘闸制动器副2的液压流体的供应。
在制动盘3的外周位置设置有测速传感器7，该测速传感器7测得的制动盘3的转速信号发送给电控设备6，电控设备6可以根据转速信号确定盘闸制动器副2是否都已经全部失效，例如根据当前的转速判断是否盘闸制动器副2并没有实现制动作用。如果确定出所有的盘闸制动器副2全部失效，则电控设备6可以对电机5发送控制信号，以便利用电机5控制卷筒1的转速以实现制动作用。
对于图4中的液压回路4，图5示出了一种与盘闸制动器副连通的液压回路的相关液压控制实例。为了描述方便，在图5中只示意性的绘出了两组盘闸制动器副，分别为盘闸制动器副9.1和9.2。盘闸制动器副9.1和9.2的油缸的有杆腔相互连通，并且经过多个电磁通断阀8.1、8.2连接到电液比例换向阀6.1、6.2，以及经过电磁通断阀8.3、8.4连接到油箱。
电液比例换向阀6.1和6.2分别与蓄能器7.1和7.2连通，同时均与油泵2.1和2.2连通。恒减速制动过程既可以通过油泵2.1和2.2向盘闸制动器副提供压力油来实现，也可以由蓄能器7.1或7.2向盘闸制动器副提供压力油实现。
举例来说，当电磁通断阀8.3通电时，盘闸制动器副9.1和9.2与油箱的连通关系被切断，此时还通过向控制电液比例换向阀6.1供以控制信号电压10V，以使得电液比例换向阀6.1工作在左位。油泵2.1泵出的压力油经由单向阀5.1、单向阀5.3进入电液比例换向阀6.1，压力油从电液比例换向阀6.1流出后，再分流到电磁通断阀8.1和8.2，然后汇合后压入盘闸制动器副9.1和9.2，实现盘闸制动器副对制动盘的制动作用。同时，压力油也会通过单向阀5.3和5.4分别流向蓄能器7.1和7.2进行压力存储。溢流阀4.1和4.2可以对油泵2.1和2.2进行系统最大压力调定，而溢流阀4.3和4.4可以分别对以及蓄能器7.1和7.2进行最大存储压力保护。
在正常的工作制动过程中，例如在矿井提升机到达停车点或者暂时停车进行检修时需要进行正常制动，这个过程通常是电机制动子系统先控制电机使提升机减速至停止，停止后利用盘闸制动子系统进行盘闸制动。盘闸制动过程可以通 过给图5中的电磁通断阀8.4通电的方式，使得盘闸制动器副9.1和9.2的油缸中的压力油流回油箱，从而实现合闸，维持矿井提升机的制动状态。
电液比例换向阀6.1和6.2分别连通着蓄能器7.1和7.2，即电液比例换向阀6.1可以接收来自蓄能器7.1的压力油，以便供应给盘闸制动器副使用，这条供应给盘闸制动器副的液压回路可以作为主用制动回路使用。在蓄能器7.1经由电液比例换向阀6.1到盘闸制动器副9.1和9.2的主用制动回路发生故障时，可以通过电液比例换向阀6.1和6.2的切换操作，实现由蓄能器7.2经由电液比例换向阀6.2向盘闸制动器副9.1和9.2供应压力油，即该条备用制动回路替代主用制动回路发挥制动作用。
当出现意外情况，如主控突然断电或失控，煤矿全部门停电，此时需要立即采取紧急安全制动。此时，电磁通断阀和电液比例换向阀的动作所需电能可由备用UPS提供，而盘闸制动器副所需的压力能由蓄能器提供。此时，电磁通断阀8.3通电，电液比例换向阀6.1的控制信号则在-10V到10V进行调整，蓄能器7.1中的压力油直接进入电液比例换向阀6.1，此时电液比例换向阀6.1在-10V到10V的之间变化的控制信号来改变通过流量，进而调整经过电液比例换向阀后的压力油的压力大小，调整压力后的压力油分别进入电磁通断阀8.1和8.2，再汇合一起压入盘闸制动器副9.1和9.2。通过对电液比例换向阀施加电流或电压控制可以改变进入到盘闸制动器副的油压，通过油压来控制施加给制动盘的压力作用，调整闸瓦对制动盘的摩擦力的大小，进而调整制动力矩的大小，实现工程提升设备的恒减速制动。
当传感单元(例如测速传感器或者压力传感器)检测到正常的恒减速制动失效或减速度误差超出允许范围的情况下，则需要启用备用制动回路来接替出现故障的主用制动回路来实现恒减速制动。同样的，备用制动回路中的电磁通断阀和电液比例换向阀动作所需的电能也可由备用UPS提供，盘闸制动器副所需的压力能由蓄能器提供。此时，可关闭电液比例换向阀6.1，并将电磁阀8.1、8.2和8.3均通电，电液比例换向阀6.2的控制信号则从-10V到10V之间调整，蓄能器7.2中的压力油直接进入电液比例换向阀6.2，此时电液比例换向阀6.2在-10V到10V的之间变化的控制信号来改变通过流量，进而调整经过电液比例换 向阀后的压力油的压力大小，调整压力后的压力油分别进入电磁通断阀8.1和8.2，再汇合一起压入盘闸制动器副9.1和9.2。
最后应当说明的是:以上实施例仅用以说明本发明的技术方案而非对其限制；尽管参照较佳实施例对本发明进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本发明的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本发明技术方案的精神，其均应涵盖在本发明请求保护的技术方案范围当中。

Claims (15)

  1. 一种安全制动控制系统，用于对工程提升设备进行安全制动控制，其特征在于，包括：
    盘闸制动子系统(100)，用于通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘(3)进行安全制动；
    电控制动子系统(200)，用于在所述盘闸制动子系统(100)的制动失效时对所述工程提升设备的电机(5)进行电机制动。
  2. 根据权利要求1所述的安全制动控制系统，其特征在于，所述盘闸制动子系统(100)包括：
    盘闸制动器组(110)，具有至少一组盘闸制动器副(2)，用于在液压流体的驱动下对所述工程提升设备的制动盘(3)进行安全制动；
    至少一组主用制动回路(120)，分别与所述盘闸制动器组(110)中的各个盘闸制动器副(2)连接，用于在所述工程提升设备需要紧急制动时，向所述盘闸制动器组(110)中对应的盘闸制动器副(2)提供控制所述盘闸制动器副(2)的制动力矩的液压流体；
    至少一组备用制动回路(130)，分别与所述盘闸制动器组(110)中的各个盘闸制动器副(2)连接，用于在所述主用制动回路(120)中的至少部分主用制动回路(120)发生故障时，通过液压回路的切换来替代发生故障的主用制动回路(120)来向对应的盘闸制动器副(2)提供控制所述盘闸制动器副(2)的制动力矩的液压流体。
  3. 根据权利要求2所述的安全制动控制系统，其特征在于，所述盘闸制动子系统(100)还包括：
    电液比例换向阀(140)，设置在所述主用制动回路(120)和所述备用制动回路(130)中，用于对所述主用制动回路(120)和所述备用制动回路(130)分别与盘闸制动器组(110)的连通关系和流量进行控制；
    检测反馈部件(150)，用于检测能够表征所述工程提升设备的运行状态的传感信号，并反馈给所述电液比例换向阀(140)和所述电控制动子系统(200)。
  4. 根据权利要求3所述的安全制动控制系统，其特征在于，所述检测反馈部件(150)包括：
    恒减压控制柜(151)，用于根据接收到的传感信号向所述电液比例换向阀(140)提供控制信号，以便对所述工程提升设备的制动盘(3)实现闭环控制方式的恒减速制动控制；
    传感单元(152)，用于检测能够表征所述工程提升设备的运行状态的传感信号，并将获得的传感信号发送给所述恒减压控制柜(151)。
  5. 根据权利要求4所述的安全制动控制系统，其特征在于，所述传感单元(152)包括以下至少一种传感器：
    压力传感器，设置在各个所述主用制动回路(120)和各个所述备用制动回路(130)中，用于检测所在液压管路的压力，并将获得的压力传感信号发送给所述恒减压控制柜(151)；
    测速传感器(7)，设置在所述工程提升设备的卷筒(1)或所述制动盘上，用于检测所述卷筒(1)或所述制动盘的转速，并将获得的转速传感信号发送给所述恒减压控制柜(151)；
    间隙/行程传感器，设置在各个盘闸制动器副(2)中，用于检测所述盘闸制动器副(2)的间隙/行程传感信号，并将所述间隙/行程传感信号发送给所述恒减压控制柜(151)。
  6. 根据权利要求3所述的安全制动控制系统，其特征在于，所述电控制动子系统(200)还用于根据所述检测反馈部件(150)反馈的传感信号判断所述盘闸制动子系统(100)中的各个主用制动回路(120)是否全部失效，如果全部失效，则对所述工程提升设备的电机(5)进行电机制动。
  7. 根据权利要求3所述的安全制动控制系统，其特征在于，所述主用制动回路(120)和备用制动回路(130)各自由独立的蓄能器供能。
  8. 根据权利要求3所述的安全制动控制系统，其特征在于，所述电液比例换向阀(140)为多个，分别设置在各个主用制动回路(120)和备用制动回路(130)中，用于通过控制每个主用制动回路(120)和备用制动回路(130)的连通关系来实现主备制动回路的切换，并通过对当前连通的制动回路的流量控制来实现对 所述工程提升设备的制动盘(3)的恒减速制动控制。
  9. 根据权利要求3所述的安全制动控制系统，其特征在于，在所述主用制动回路(120)和所述备用制动回路(130)中还包括控制液压流体的连通关系的电磁通断阀组，用于控制所述主用制动回路(120)或备用制动回路(130)的通断，并实现所述盘闸制动器组(110)的卸压控制。
  10. 根据权利要求9所述的安全制动控制系统，其特征在于，所述电磁通断阀组、电液比例换向阀(140)和检测反馈部件(150)在紧急安全制动状况下由备用不间断供电系统供电。
  11. 一种矿井提升机，其特征在于，包括权利要求1～10任一项所述的安全制动控制系统，所述矿井提升机为所述工程提升设备。
  12. 一种基于权利要求1～10任一项所述的安全制动控制系统的安全制动控制方法，其特征在于，包括：
    在工程提升设备紧急安全制动时，盘闸制动子系统(100)通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘(3)进行安全制动；
    当所述盘闸制动子系统(100)的制动失效时，电控制动子系统(200)对所述工程提升设备的电机(5)进行电机制动。
  13. 根据权利要求12所述的安全制动控制方法，其特征在于，所述盘闸制动子系统(100)包括：具有至少一组盘闸制动器副(2)的盘闸制动器组(110)、分别与所述盘闸制动器组(110)中的各个盘闸制动器副(2)连接的至少一组主用制动回路(120)和至少一组备用制动回路(130)；所述盘闸制动子系统(100)通过液压流体驱动制动器的闸瓦对所述工程提升设备的制动盘(3)进行安全制动的操作具体包括：
    所述至少一组主用制动回路(120)向所述盘闸制动器组(110)中对应的盘闸制动器副(2)提供控制所述盘闸制动器副(2)的制动力矩的液压流体，以使对应的盘闸制动器副(2)在液压流体的驱动下对所述工程提升设备的制动盘(3)进行安全制动；
    在所述主用制动回路(120)中的至少部分主用制动回路(120)发生故障时，所述至少一组备用制动回路(130)通过液压回路的切换来替代发生故障的 主用制动回路(120)来向对应的盘闸制动器副(2)提供控制所述盘闸制动器副(2)的制动力矩的液压流体。
  14. 根据权利要求13所述的安全制动控制方法，其特征在于，还包括：当所述盘闸制动子系统(100)中的各个主用制动回路(120)全部失效时，所述电控制动子系统(200)对所述工程提升设备的电机(5)进行电机制动。
  15. 根据权利要求13所述的安全制动控制方法，其特征在于，所述盘闸制动子系统(100)还包括：检测反馈部件(150)、分别设置在各个主用制动回路(120)和备用制动回路(130)中的多个电液比例换向阀(140)；
    所述安全制动控制方法还包括：
    所述电液比例换向阀根据所述检测反馈部件(150)检测到的能够表征所述工程提升设备的运行状态的传感信号，控制每个主用制动回路(120)和备用制动回路(130)的连通关系来实现主备制动回路的切换，并通过对当前连通的制动回路的流量控制来实现对所述工程提升设备的制动盘(3)的恒减速制动控制。
PCT/CN2016/104638 2016-11-04 2016-11-04 安全制动控制系统、矿井提升机和安全制动控制方法 WO2018082022A1 (zh)

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