CN110843740A - Hydraulic-mechanical combined braking system for coal mine articulated explosion-proof vehicle - Google Patents
Hydraulic-mechanical combined braking system for coal mine articulated explosion-proof vehicle Download PDFInfo
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- CN110843740A CN110843740A CN201911023244.0A CN201911023244A CN110843740A CN 110843740 A CN110843740 A CN 110843740A CN 201911023244 A CN201911023244 A CN 201911023244A CN 110843740 A CN110843740 A CN 110843740A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/062—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels acting on transmission parts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T5/00—Vehicle modifications to facilitate cooling of brakes
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- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
The invention belongs to the technical field of underground auxiliary transportation equipment of coal mines, and particularly relates to a hydraulic-mechanical combined braking system for a coal mine articulated explosion-proof vehicle. The hydraulic torque converter is connected with a gearbox through an upper transmission shaft, the front output of the gearbox is connected with a front axle through a front axle transmission shaft, two ends of the front axle are respectively connected with two wet-type service brakes, the rear output of the gearbox is connected with a connecting flange of a hydraulic retarding brake device through a hinged transmission shaft, a connecting flange of the hydraulic retarding brake device is connected with a rear axle through a rear axle transmission shaft, two ends of the rear axle are respectively connected with the two wet-type service brakes, wet-type parking brakes are arranged on two shafts of the gearbox, the four wet-type service brakes on the front axle and the rear axle are respectively connected with a mechanical brake service brake control valve and a switching valve through hydraulic control pipelines, the switching valve is connected with a hydraulic brake control system, and the hydraulic retarding brake device is connected with an air source through a pneumatic control valve and a pneumatic control pipeline.
Description
Technical Field
The invention belongs to the technical field of underground auxiliary transportation equipment of coal mines, and particularly relates to a hydraulic-mechanical combined braking system for a coal mine articulated explosion-proof vehicle.
Background
With the rapid development of mining technology in China, mining areas of nearly horizontal coal seams are gradually reduced, inclined coal seams are gradually increased, and the traveling gradient and the ramp distance of a trackless auxiliary transport vehicle are gradually increased. The prior explosion-proof vehicle for underground auxiliary transportation of coal mines is divided into an articulated explosion-proof vehicle and an integral explosion-proof vehicle according to the frame type, the power transmission mode and the braking system of the two types of vehicles are different, the articulated explosion-proof vehicle adopts front and rear articulated frames, generally adapts to a slope of less than 10 degrees, and has a transportation distance of no more than 500m, however, in many mines in northern Shanxi, Shandong Yanzhou, Gansu and the like, the slope gradient of the auxiliary transportation slope reaches 10-14 degrees, and the slope distance exceeds 2000m, so that a severe test is formed on the braking performance of the vehicle.
At present, the articulated explosion-proof vehicle used only depends on single mechanical friction braking, and under the condition of long distance and large gradient, the temperature rise of oil liquid during braking is too fast and the braking friction heat cannot be taken away in time, so that the serious problems of frequent overheating of the brake, sealing failure, oil leakage, excessive abrasion of a friction plate, reduction of braking efficiency and the like occur, and potential safety hazards are brought to the production and operation of coal mines.
Disclosure of Invention
The invention provides a hydraulic-mechanical combined braking system for a coal mine articulated explosion-proof vehicle, which aims to solve the problems that the temperature rise of brake oil is too fast and the brake friction heat cannot be taken away in time due to the fact that the existing coal mine articulated explosion-proof vehicle is braked by only single mechanical friction under the long-distance and large-gradient running condition, so that the brake is overheated frequently, the sealing is failed, the oil leaks, friction plates are excessively worn, the braking efficiency is reduced, and the like.
The invention adopts the following technical scheme: a hydraulic-mechanical combined braking system for a coal mine articulated explosion-proof vehicle comprises a hydraulic torque converter connected with the rear part of an engine, wherein the hydraulic torque converter is connected with a gearbox through an upper transmission shaft, the front output of the gearbox is connected with a front axle through a front axle transmission shaft, two ends of the front axle are respectively connected with two wet-type service brakes, the rear output of the gearbox is connected with a connecting flange of a hydraulic retarding braking device through an articulated transmission shaft, the connecting flange of the hydraulic retarding braking device is connected with a rear axle through a rear axle transmission shaft, two ends of the rear axle are respectively connected with the two wet-type service brakes, a wet-type parking brake is arranged on a second axle of the gearbox, the hydraulic retarding braking device is connected with a water-cooling oil heat exchanger through a metal hose, the water-cooling oil heat exchanger is connected with a radiator through a; the four wet service brakes on the front axle and the rear axle are respectively connected with a mechanical brake service brake control valve and a switching valve through hydraulic control pipelines, the switching valve is connected with a hydraulic brake control system, and the hydraulic retarding brake device is connected with an air source through a pneumatic control valve and a pneumatic control pipeline.
Furthermore, the hydraulic retarding brake device comprises a connecting flange, a cover, a shell, a rotor impeller, a stator impeller, a main shaft, an oil storage cavity and a control valve, wherein the cover and the shell form a structure in which the hydraulic working cavity is arranged, the hydraulic working cavity is communicated with the oil storage cavity, and the oil storage cavity is connected with a metal hose through the control valve; a rotor impeller and a stator impeller are arranged in the hydraulic working cavity, the rotor impeller is driven to rotate by a main shaft, and a connecting flange is arranged at the end part of the main shaft. The hydraulic retarding brake device is designed in a split mode and is divided into a retarding device main body and a heat exchanger portion, the retarding device main body and the heat exchanger portion are connected through a metal hose penetrating through a hinge center, the heat exchanger portion is arranged on the hinge front portion, the main body is arranged on the rear portion of a hinge portion of a vehicle and mounted on the rear portion of a hinge transmission shaft, the front portion of the hinge transmission shaft is connected with a rear output flange of a power shifting gearbox, a front output flange of the power shifting gearbox is connected with a front drive axle input flange, an input flange of the power shifting gearbox is connected with an output flange of a. The hydraulic retarder is a flexible braking device which takes oil as a working medium and converts vehicle kinetic energy into oil heat energy through liquid damping to achieve the effect of deceleration braking, the front end and the rear end of the flexible braking device are respectively connected with a gearbox and a drive axle through a transmission shaft, the hydraulic retarder generates braking force through the action of oil damping by opening and closing a pneumatic control braking function and the magnitude of braking torque, and heat generated by braking is dissipated through a water cooling mode.
Furthermore, the wet-type service brake comprises a bearing I, a static shell, a shoulder bolt, a disc spring group, a floating oil seal, a piston, an inner friction plate, an outer friction plate, a pressure plate, a movable shell, an end cover, a nut I, a bearing II, a screw plug, a shaft and a nut II; quiet shell and front axle or rear axle housing fixed connection, the pressure disk passes through the bolt to be connected with quiet shell, the axle passes through bearing I and bearing II and connects and supports the movable casing, both ends are fastened through nut I and nut II respectively about the axle, interior friction disc passes through internal tooth and quiet shell fixed connection, the outer friction disc passes through the external tooth and is connected with the movable casing, and rotate in step with the movable casing, be provided with floating oil blanket between quiet shell and the movable casing, the movable casing right side is connected with the end cover, the plug screw is installed in quiet shell bottom, interior friction disc and outer friction disc interval set up, interior friction disc left side is provided with the piston, the piston left side sets up the dish spring group of compressed, the dish spring group sets up on the shoulder bolt. The wet-type service brake is arranged at four wheel edges of the whole vehicle, the brake is a fully-closed wet-type brake, the brake mode is hydraulic brake, and a spring is released, so that the service brake function of the whole vehicle is realized. The static shell of the brake is rigidly connected with the axle housing of the drive axle, the dynamic shell of the brake is connected with the tire, parts such as a fixed friction plate, a dynamic friction plate, a piston and the like are arranged between the dynamic shell and the static shell, and hydraulic oil pushes the piston to compress the friction plate during braking, so that the vehicle braking is realized. The above parts are all sealed in oil liquid, so as to achieve the functions of heat dissipation and protection.
Furthermore, the wet parking brake comprises a spring shell, a disc spring, a sealing shell, a piston, an emptying nozzle assembly, a vent plug assembly, a friction plate shell, a powder sheet and a steel sheet, wherein the friction plate shell of the parking brake is connected with the shell of the gearbox, the spring shell and the sealing shell are connected into a whole with the friction plate shell through a long bolt, the disc spring is installed in a high-pressure oil cavity formed by the spring shell and the sealing shell, the piston is installed on the right side of the disc spring, the right side of the piston is in contact connection with the powder sheet, the powder sheet is connected with the gearbox shaft through inner teeth and rotates along with the gearbox, the steel sheet is fixedly connected with the friction plate shell through outer teeth, the powder sheet and the steel sheet are arranged in a friction plate lubricating oil cavity at intervals, the emptying nozzle assembly is communicated. The wet type parking brake is arranged on the power gear shifting gearbox, the brake is a fully-closed wet type brake, the braking mode is spring braking, hydraulic pressure is released, and the brake is used for achieving the parking braking function of the whole vehicle. The static shell of the brake is rigidly connected with the shell of the gearbox, the dynamic shell of the brake is connected with the rotating shaft of the gearbox, a fixed friction plate, a dynamic friction plate, a disc spring and other parts are arranged between the dynamic shell and the static shell, the friction plate is pressed by the spring force generated by the disc spring during parking to realize parking braking, and hydraulic oil pushes the disc spring to deform during driving so that the friction plate is separated and the parking braking is released. The above parts are all sealed in oil liquid, so as to achieve the functions of heat dissipation and protection.
The hydraulic brake control system comprises an air storage tank, a safety valve, a knob switch valve, a gear control valve, a pilot-controlled gas proportional pressure reducing valve, a one-way valve I, a one-way valve II, a pressure regulating valve I, a pressure regulating valve II, a shuttle valve I, a shuttle valve II, a control valve, an oil-gas separation device, an exhaust pipe, an exhaust valve, a hydraulic working cavity and an oil pool, wherein a K port of the pilot-controlled gas proportional pressure reducing valve is connected with the mechanical brake control system through a mechanical independent brake switching valve, a P port of the pilot-controlled gas proportional pressure reducing valve is connected with the air storage tank through the safety valve, a water discharge switch is arranged at the bottom of the air storage tank, an A port of the pilot-controlled gas proportional pressure reducing valve is connected with a P1 port of the shuttle valve II, a P2 port of the shuttle valve II is connected with an A port of the shuttle valve I, a P1 port of the shuttle valve I is connected with the pressure regulating valve I, the pressure regulating valve I is, the pressure regulating valve II is connected with a one-way valve II in parallel; the P port of the gear control valve is connected with the A port of the knob switch valve, and the P port of the knob switch valve is connected with the gas storage tank; the port A of the shuttle valve II is connected with the port P and the port K of the control valve, the port A of the control valve is connected with the oil pool, the port R of the control valve is connected with the inlet of the oil-gas separation device, the exhaust pipe is arranged on the exhaust port of the oil-gas separation device, the outlet of the oil-gas separation device is connected with the hydraulic working cavity through the exhaust valve, and the hydraulic working cavity is connected with the oil pool.
The mechanical brake control system comprises a serial double-loop brake valve, an energy accumulator I, an energy accumulator II, a liquid charging valve, a hydraulic pump, a one-way valve III, a parking brake valve and a manual pump, wherein pressure oil of the hydraulic pump is divided into two paths, one path of pressure oil is connected with a port P of the liquid charging valve, and two outlets A1 and A2 of the liquid charging valve are respectively connected with the energy accumulator I and the energy accumulator II; the other path is connected with a P port of a safety valve, a T port of the safety valve is respectively connected with an oil tank and a T1 port of a tandem type double-loop brake valve, an A1 port and an A2 port of the tandem type double-loop brake valve are respectively connected with a front wheel service brake and a rear wheel service brake, a P2 port of the tandem type double-loop brake valve is connected with a P port of a parking brake valve through a one-way valve III, an A2 port of the tandem type double-loop brake valve is connected with a P port of a mechanical independent brake switching valve, a T port of the mechanical independent brake switching valve is connected with the oil tank, and an A port of the mechanical independent brake switching valve is connected with a.
The invention has two brake functions of mechanical friction brake and hydraulic damping brake, wherein the mechanical friction brake generates brake force through mechanical friction force, and the size of the brake force is determined by the hydraulic pressure of the pedal brake valve; the hydraulic damping brake converts the vehicle running kinetic energy into oil liquid heat energy through the hydraulic damping action to generate braking force, and then the heat energy is dissipated through the water cooling action, and the magnitude of the braking force is determined by the pneumatic pressure output by the pneumatic control valve. The combined brake system is provided with two working modes, namely an independent braking mode and a combined braking mode, and the two working modes can work independently and jointly. The vehicle is in long distance heavy grade downhill path operating mode, select the independent braking mode, the exclusive use hydraulic braking, need not use mechanical friction braking, reach the effect that the vehicle ramp is fast to go, the exclusive use mechanical friction braking again when needing the vehicle to stop, thereby protection mechanical brake, simultaneously can be according to different slopes and the different speed of a motor vehicle that needs, the different hydraulic braking gear of transform, hydraulic braking is flexible braking function, braking process and braking gear transform are more smooth-going stable. When the vehicle is quickly braked during flat road running, a combined braking mode is selected, mechanical braking and hydraulic braking can be simultaneously controlled to play a role by operating the foot brake valve, the mechanical braking force and the hydraulic braking force are proportionally increased along with the increase of braking pressure, the braking force of the whole vehicle is the sum of the mechanical braking force and the hydraulic braking force, and the optimal braking effect can be achieved.
Compared with the prior art, the invention has the following beneficial effects:
1. the hydraulic-mechanical combined braking system for the coal mine articulated explosion-proof vehicle has two braking functions of mechanical friction braking and hydraulic retarding braking, and the two braking functions are cooperated to realize combined braking, so that the braking efficiency of the whole vehicle is improved, a mechanical brake is protected, the safety and stable speed running of a vehicle ramp is ensured, and the problem that the safety accident is easily caused due to the frequent mechanical rigid brake failure of the existing coal mine vehicle in a long-distance and large-angle ramp is solved.
2. When the vehicle runs on a flat road, the hydraulic-mechanical combined braking system has high braking rate and enough safety margin, realizes shorter braking distance, can simultaneously step on a mechanical braking brake and manually control hydraulic braking during braking, performs combined braking, and completes braking with the shortest distance. The work of the hydraulic retarder enables the service brake to be kept in a cold state, so that the maximum braking effect is realized.
3. When the vehicle descends on a long-distance slope, the hydraulic retarding braking can keep the vehicle running at a stable speed through a flexible speed-stabilizing braking technology, pedal mechanical rigid braking is not needed, the running safety and stability of the vehicle can be improved, and the fatigue degree of a driver can be reduced.
4. The hydraulic retarding brake device is a wear-free product, the braking process is smooth and stable, fewer gearboxes are required for gear shifting and downshifting, the impact of the hydraulic retarding brake device on a vehicle is smaller due to the reduction of power interruption, the hydraulic retarding brake device cannot be locked suddenly, the comfort and the stability of the driving of the whole vehicle are improved, and the psychological pressure of downhill driving caused by brake failure, failure and the like due to the fact that a driver fears heating when the driver is in a long slope underground a coal mine is also effectively relieved.
5. After the hydraulic-mechanical combined braking system is adopted by the vehicle, the braking times and time are greatly reduced, the average speed of the vehicle is improved, the use of the working gear of the gearbox can be reduced by 90%, the service life is prolonged, and the oil consumption of an engine is reduced.
Drawings
FIG. 1 is a schematic diagram of a hydraulic-mechanical combined braking system for a coal mine articulated explosion-proof vehicle according to the invention;
FIG. 2 is a schematic view of a hydraulic retarder braking device;
FIG. 3 is a schematic structural view of a wet wheel-side service brake;
FIG. 4 is a schematic structural diagram of a wet parking brake;
FIG. 5 is a schematic diagram of a combined brake control system;
FIG. 6 is a schematic diagram of an integrated engine and hydraulic brake cooling system;
in the figure, 1, an expansion water tank, 2, a radiator, 3, an engine device, 4, a hydraulic torque converter, 5, a front axle, 6, a water-cooled oil heat exchanger, 7, a wet parking brake, 8, a power shifting gearbox, 9, an articulated transmission shaft, 10, a hydraulic retarder brake device, 11, a rear axle transmission shaft, 12, a wet service brake, 13, a rear axle, 14, a mechanical independent brake switching valve, 15, a pneumatic control valve, 16, a mechanical brake service brake control valve, 17, an upper transmission shaft, 18, a front axle transmission shaft, 19, a mechanical parking brake control valve, 20, a connecting flange, 21, an exhaust valve, 22, a shell, 23, a rotor impeller, 24, a stator impeller, 25, a main shaft, 26, a hydraulic working chamber, 27, an oil storage chamber, 28, a control valve, 29, a bearing, 30, a static shell, 31, a shoulder bolt, 32, a disc spring set, 33, a floating oil seal, 34. piston, 35, inner friction plate, 36, outer friction plate, 37, pressure plate, 38, movable shell, 39, end cover, 40, nut I, 41, bearing, 42, screw plug, 43, shaft, 44, nut II, 45, spring shell, 46, disc spring, 47, seal shell, 48, piston, 49, emptying nozzle assembly, 50, vent plug assembly, 51, friction plate shell, 52, powder sheet, 53, steel sheet, 54, screw plug, 55, gasket, 56, front wheel service brake, 57, rear wheel service brake, 58, series type double-circuit brake valve, 59, accumulator I, 60, accumulator II, 61, liquid filling valve, 62, hydraulic pump, 63, check valve III, 64, parking brake valve, 65, manual pump, 66, parking brake, 67, gas storage tank, 68, drain switch, 69, safety valve, 70, rotary switch valve, 71, shift position control valve, 72, gas proportional hydraulic pressure reducing valve, 73. the hydraulic brake system comprises check valves I and 75, check valves II and 74, pressure regulating valves I and 76, pressure regulating valves II and 77, shuttle valves I and 78, shuttle valves II and 79, control valves 80, an oil-gas separation device 81, an exhaust pipe 82, an oil pool 83, an oil pipe 84, a thermostat 85, a water pipeline 86, a hydraulic brake oil pipeline 87 and a circulating water pump.
Detailed Description
The embodiments of the present invention will be further explained with reference to the drawings.
The invention relates to a hydraulic-mechanical combined braking system for a coal mine articulated explosion-proof vehicle, which is characterized in that the system can realize two functions of hydraulic damping braking and mechanical friction braking, and the two braking functions are combined to act, so that the system can be applied to the coal mine articulated explosion-proof vehicle, and can effectively improve the braking safety, reliability, smoothness and operation comfort of the whole vehicle under different running conditions, especially under the long-distance and large-gradient conditions. The system mainly comprises a hydraulic retarding brake device for realizing hydraulic damping braking, a wet-type service brake and a parking brake for realizing mechanical friction braking, a hydraulic control system for controlling the combined braking system and an integrated cooling system for simultaneously realizing engine cooling and hydraulic braking cooling. The engine 3 is arranged at the hinged front part of the vehicle, the rear part of the engine 3 is connected with a hydraulic torque converter 4, the hydraulic torque converter 4 is connected with a gearbox 8 through an upper transmission shaft 17, the front output of the gearbox 8 is connected with a front axle 5 through a front axle transmission shaft 18, two ends of the front axle 5 are respectively connected with two wet-type service brakes 12, the rear output of the gearbox 8 is connected with a front flange of a hydraulic retarding brake device 10 through a hinged transmission shaft 9, a rear flange of the hydraulic retarding brake device 10 is connected with a rear axle 13 through a rear axle transmission shaft 11, two ends of the rear axle 13 are respectively connected with the two wet-type service brakes 12, a wet-type parking brake 7 is arranged on two shafts of the gearbox 8, the hydraulic retarding brake device 10 is connected with a water-cooling oil heat exchanger 6 through a metal hose, the water-cooling oil heat exchanger 6 is. The combined brake system is provided with two working modes of independent brake and combined brake, when the independent working mode is selected by operating the switching valve 14, a driver controls the hydraulic brake system by operating the pneumatic control valve 15, so that the hydraulic retarder brake device 10 generates hydraulic brake force, and the force is transmitted to wheels through the transmission shaft, the gearbox 8, the front axle 5 and the rear axle 13, so as to realize the hydraulic brake function; the driver controls the mechanical brake system by operating the mechanical brake service brake control valve 16 and the mechanical parking brake control valve 19, so that the wet service brake 12 generates service brake force, the force directly acts on the wheels, and the wet parking brake 7 generates parking brake force, the force is transmitted to the wheels through the gearbox 8, the transmission shafts 9, 11 and 18, the front axle 5 and the rear axle 13, and the mechanical parking brake function is realized. When the combined braking mode is selected by operating the switching valve 14, the driver can simultaneously control the hydraulic braking function and the mechanical braking function by operating the hydraulic mechanical traveling switching valve 12, and the hydraulic braking function and the mechanical braking function are cooperatively acted.
When the vehicle runs on a downhill, the hydraulic brake function can be independently used, the hydraulic brake function has three working gears of 0 gear, 1 gear and 2 gears, the output of 0%, 50% and 100% brake force is respectively realized, a driver selects a proper brake gear by dialing the pneumatic control valve 15 according to different gradients and required vehicle speeds, and the brake gear can be changed in real time. After hydraulic braking is adopted, a driver can control the steering wheel to run, and long-time continuous braking is avoided. When the vehicle needs to be stopped, the mechanical brake is executed through the pedal mechanical brake service brake control valve 16, the vehicle is stopped, and the long-time continuous use of the mechanical brake is avoided, so that the mechanical brake is protected, the brake smoothness and stability are improved, and the operation labor intensity of a driver is reduced.
When the vehicle is braked rapidly in the flat road running process, the switching valve 14 is operated to select a combined brake mode, so that the hydraulic brake and mechanical brake linkage control and combined action are realized, during the braking process, the service brake control valve 16 of the pedal mechanical brake service can simultaneously control two brake functions, the hydraulic brake force and the mechanical brake force are proportionally increased or reduced along with the execution stroke of the service brake control valve 16 of the mechanical brake service, the two brake forces are simultaneously acted, the vehicle brake is realized with the minimum brake distance and time, the best brake effect is achieved, and the brake safety and reliability are improved.
As shown in fig. 2, the hydraulic slow braking device is characterized in that a split design is adopted, a main body of the device is arranged at the rear part of a vehicle hinged part, a water-cooling oil heat exchanger is arranged at the front part of the hinged part, the device is a flexible braking device for converting mechanical energy into liquid heat energy and mainly comprises a connecting flange 20, a cover 21, a shell 22, a rotor impeller 23, a stator impeller 24, a main shaft 25, a hydraulic working chamber 26, an oil storage chamber 27 and a control valve 28, two impellers, namely a driven rotor impeller 23 and a fixed stator impeller 24, are arranged in the hydraulic slow braking device, and the rotor impeller is connected with a vehicle transmission shaft through the main shaft 25 and the connecting flange 20 and synchronously rotates. When the hydraulic retarding brake device is started, compressed air enters the oil storage cavity 27 through the control port, working oil in the oil storage cavity 27 is pressed into the hydraulic working cavity 26 through an oil way, and the rotor impeller 23 drives the oil to rotate around the axis; simultaneously, the oil moves in the direction of the vanes, throwing towards the stator impeller 24. The stator impeller blades generate reaction to oil, and the oil flows out of the stator and then is rotated back to impact the rotor impeller 23, so that resistance moment to the rotor is formed, the rotation of the rotor is blocked, and the deceleration braking effect on the vehicle is realized. The oil filling amount entering the hydraulic working chamber can be controlled by controlling the pressure of the compressed air in the oil storage chamber 27, so that the braking torque output by the hydraulic retarding braking device is controlled.
As shown in fig. 3, the mechanical brake totally-enclosed wet service brake adopts hydraulic brake and spring release, and is used for realizing service brake of a whole vehicle. And simultaneously plays a role in protection and cooling. The hydraulic oil-gas separating device mainly comprises a bearing 29, a static shell 30, a shoulder bolt 31, a disc spring group 32, a floating oil seal 33, a piston 34, an inner friction plate 35, an outer friction plate 36, a pressure plate 37, a movable shell 38, an end cover 39, a nut I40, a bearing 41, a screw plug 42, a shaft 43 and a nut II 44. Quiet shell 30 and front axle 5, rear axle 13 shell connection, it is immobile, pressure disk 37 passes through the bolt and is connected with quiet shell 30, axle 43 passes through bearing 29, bearing 41 will move shell 38 and connect and support, both ends are respectively through nut I40 about the axle, nut II 44 fastens, inner friction piece 35 passes through the internal tooth and is connected with quiet shell 30, it is immobile, outer friction piece 36 passes through the external tooth and is connected with moving shell 38, and with move shell synchronous rotation, be provided with floating oil seal 33 between quiet shell 30 and the moving shell 38, quiet shell 30 right side is connected with end cover 39, play sealed and guard action, plug screw 42 is installed in quiet shell 30 bottom, be used for the oil drain. When braking is carried out, high-pressure oil enters a braking oil cavity to push a piston 34 to the right, a disc spring group 32 installed on a shoulder bolt 31 is compressed, meanwhile, the piston 34 presses an outer friction plate 36 rotating synchronously with a vehicle and an inner friction plate 35 which is fixed, the vehicle is braked by the generated friction force, when the braking is released, the high-pressure oil is withdrawn, the piston 34 is pushed to the left by the spring force generated by the disc spring group 32, the inner friction plate 35 is separated from the outer friction plate 36, and the braking is released.
As shown in fig. 4, the mechanical braking totally-enclosed wet parking brake adopts spring braking and hydraulic release, and is used for realizing parking braking of a whole vehicle. And simultaneously plays a role in protection and cooling. Mainly comprises a spring shell 45, a disc spring 46, a sealing shell 47, a piston 48, an emptying nozzle assembly 49, a vent plug assembly 50, a friction sheet shell 51, a powder sheet 52, a steel sheet 53, a screw plug 54 and a gasket 55. A friction plate shell 51 of the parking brake is connected with a gearbox shell, a spring shell 45 and a sealing shell 47 are connected with the friction plate shell 51 into a whole through a long bolt, a disc spring 46 is installed in the spring shell 45, a powder sheet 52 is connected with the gearbox shaft through inner teeth and rotates along with the gearbox, a steel sheet 53 is connected with the friction plate shell 51 through outer teeth and is fixed, an emptying nozzle assembly 49 is communicated with a high-pressure oil cavity, and a breather plug assembly 50 is communicated with a friction plate lubricating oil cavity. When the vehicle is parked, the disc spring 46 pushes the piston 48 rightwards through spring force, the piston 48 presses the powder sheet 52 and the steel sheet 53 tightly, the generated friction force fixes the gearbox shaft, the parking function of the vehicle is achieved, when the parking brake of the vehicle is released, high-pressure oil enters the brake release oil cavity to push the piston 48 to move leftwards, the piston 48 compresses the disc spring 46, the powder sheet 52 is separated from the steel sheet 53, and the parking brake force is released.
FIG. 5 shows a schematic diagram of a combined brake control system, the hydraulic brake control system includes an air tank 67, a relief valve 69, a knob switch valve 70, a shift control valve 71, a pilot-controlled air proportional pressure reducing valve 72, a check valve I73, a check valve II75, a pressure regulating valve I74, a pressure regulating valve II76, a shuttle valve I77, a shuttle valve II78, a control valve 79, an oil-gas separation device 80, an exhaust pipe 81, an exhaust valve 21, a hydraulic working chamber 26 and an oil sump 82, the K port of the pilot-controlled air proportional pressure reducing valve 72 is connected to the mechanical brake control system through a mechanically independent brake switching valve 14, the P port of the pilot-controlled air proportional pressure reducing valve 72 is connected to the air tank 67 through the relief valve 69, the bottom of the air tank 67 is provided with a drain switch 68, the A port of the pilot-controlled air proportional pressure reducing valve 72 is connected to the P1 port of the shuttle valve II78, the P2 port of the shuttle valve II78 is connected to the A port of the shuttle valve I77, the P port 1 port of the shuttle valve I77 is connected to the, a P2 port of the shuttle valve I77 is connected with a pressure regulating valve II76, a pressure regulating valve II76 is connected with a port A of the gear control valve 71, and a check valve II75 is connected in parallel with the pressure regulating valve II 76; the port P of the gear control valve 71 is connected with the port A of the knob switch valve 70, and the port P of the knob switch valve 70 is connected with the air storage tank 67; the port A of the shuttle valve II77 is connected with the port P and the port K of the control valve 79, the port A of the control valve 79 is connected with the oil pool 82, the port R of the control valve 79 is connected with the inlet of the oil-gas separation device 80, the exhaust port of the oil-gas separation device 80 is provided with an exhaust pipe 81, the outlet of the oil-gas separation device 80 is connected with the hydraulic working cavity 26 through the exhaust valve 21, and the hydraulic working cavity 26 is connected with the oil pool 82.
The mechanical brake control system comprises a tandem type double-loop brake valve 58, an accumulator I59, an accumulator II60, a charging valve 61, a hydraulic pump 62, a one-way valve III63, a parking brake valve 64 and a manual pump 65, pressure oil of the hydraulic pump 62 is divided into two paths, one path is connected with a port P of the charging valve 61, and two outlets A1 and A2 of the charging valve 61 are respectively connected with the accumulator I59 and the accumulator II 60; the other path is connected with a port P of a safety valve, a port T of the safety valve is respectively connected with a fuel tank and a port T1 of a tandem type double-circuit brake valve 58, a port A1 and a port A2 of the tandem type double-circuit brake valve 58 are respectively connected with a front wheel service brake 56 and a rear wheel service brake 57, a port P2 of the tandem type double-circuit brake valve 58 is connected with a port P of a parking brake valve 64 through a one-way valve III63, a port A2 of the tandem type double-circuit brake valve 58 is connected with a port P of a mechanical independent brake switching valve 14, a port T of the mechanical independent brake switching valve 14 is connected with the fuel tank, and a port A of the mechanical independent brake switching valve 14 is connected with a.
The hydraulic-mechanical combined brake system can realize two working modes of independent braking and combined braking, wherein the independent braking mode is that hydraulic braking and mechanical braking respectively and independently work, the combined braking mode is that hydraulic braking and mechanical braking jointly and cooperatively work, specifically, the working modes are switched by operating the mechanical independent brake switching valve 14, when the mechanical independent brake switching valve 14 is at the lower position as shown in the figure, the mechanical independent brake switching valve is in the independent braking working mode, the hydraulic braking and the mechanical braking respectively and independently work, and when the mechanical independent brake switching valve 14 is operated to move to the upper position, the hydraulic braking and the mechanical braking jointly and cooperatively work. The specific braking working principle is as follows:
(1) mechanical braking system principle:
the hydraulic pump 62 is driven by the engine, and after the engine is started, the hydraulic pump is operated; the liquid charging valve 61 adopts a double-loop liquid charging valve which is mainly used for charging the energy accumulator and controlling the charging pressure of the energy accumulator; the energy accumulator I59 and the energy accumulator II60 are mainly used for storing and releasing hydraulic energy required by braking, stabilizing the braking oil pressure and ensuring a large amount of oil supply during continuous stepping braking, and respectively control the braking of the front wheel and the rear wheel, and are mutually independent; the primary function of the tandem dual circuit brake valve 58 is to control the proportional admission of pressurized oil from the accumulator to the front and rear wheel service brakes to effect vehicle braking, with the other brake circuit still operating if one of the front or rear wheel brake circuits fails. The front and rear wheel brakes 56 are mechanical wet service brakes, and the service brakes adopt the principles of hydraulic braking and spring release.
During service braking, when the pedal of the double-loop brake valve 58 is stepped, pressure oil in the two energy accumulators respectively enters the front service brake and the rear service brake through the upper cavity and the lower cavity of the valve, the pressure oil acts on a brake piston to press the friction plates to brake wheels, and the output brake pressure is proportional to the angle of the stepped brake pedal. When the pedal is released, the high-pressure oil in the brake flows back to the oil tank to release the brake.
When the parking brake is released, a path of pressure oil is led out from the accumulator 59 to the parking brake valve 64 through the check valve 63, and the output pressure of the parking brake valve 64 is a certain value and acts on the brake piston of the wet parking brake 66. The parking brake 66 is in a spring brake state when the parking brake valve does not output pressure, and when the parking brake valve is actuated, a certain pressure is output to act on the parking brake piston, and the spring is compressed to overcome the spring force to release the brake.
The manual pump 65 manually releases the parking brake to tow the vehicle when the vehicle is out of order or power is lost.
(2) Principle of hydraulic brake system
The hydraulic brake adopts pneumatic control and can realize linkage with mechanical brake at the same time. The key element of the hydraulic brake is a hydraulic retarding brake device, and the amount of oil applied to the hydraulic retarding brake device determines the magnitude of the braking force of the hydraulic retarding brake device. The hydraulic retarder braking device adopts pneumatic control.
The hydraulic retarding brake device has pneumatic control, and the hydraulic retarding brake device has two-gear control and automatic linkage control.
The manual control is that only hydraulic braking deceleration is needed and mechanical braking is not adopted in the running process of the explosion-proof vehicle, a pneumatic knob switch valve 70 is arranged in the circuit, the knob valve is opened to be in a first gear, and after the gear control valve 71 is operated, the second gear can be switched. The two gears are mainly realized by setting different pressures by the two pressure regulating valves I74 and II 76. The specific working principle is as follows:
the compressed air pressure in the air tank is maintained at 0.6-0.8 MPa, the shown position is the state that the hydraulic retarding brake is not used, and the compressed air is sealed at the knob switch valve 70. When hydraulic braking is needed, the knob switch valve 70 is opened to work at the left position, at this time, compressed air flows to the port A through the port P, the gear control valve works at the right position, the port P is communicated with the port A, the pressure is reduced by the pressure regulating valve 76 and then reaches the port P2 of the shuttle valve 77, the set pressure of the pressure reducing valve 76 is 0.15MPa, and the hydraulic retarding braking device works at the first gear. The compressed air passes through the port A of the shuttle valve, passes through the port P2 of the shuttle valve 78, reaches the port A, then reaches the port P of the pressure port of the control valve 79, one way reaches the control port K of the control valve 79 to enable the control valve to work at the upper position, the compressed air passes through the port P to the port A and enters the control port K of the oil sump 82, the oil is compressed, and the oil enters the hydraulic working chamber 26 of the hydraulic retarder braking device through the oil pipe 83.
The amount of oil entering the hydraulic working chamber 26 is determined by the pressure of the compressed air at the control port K. When the braking force needs to be increased, the gear control valve 71 is operated to work at the left position, at this time, compressed air passes through the knob switch valve 70, reaches B through the P port, reaches P1 of the shuttle valve 77 through the pressure reducing valve 74, passes through P2 of the shuttle valve 78 to A port after the P1 port reaches A port, and enters a control port K of the oil sump 82 through the control valve 79, the set pressure of the pressure reducing valve 74 is 0.3MPa, so that the oil amount entering the hydraulic retarding brake device is increased, and the pressure of P2 passes through the check valve 75 and the gear control valves A to R to exhaust.
When the operation of the retarder brake is not required, the knob switch valve 70 is turned off, and the compressed air of the pressure port P4 of the control valve 79 is exhausted through the shuttle valve 78, the shuttle valve 77, the check valve 73, the shift control valve 71 and the knob switch valve 70. Meanwhile, the pressure of the control port K of the control valve 79 disappears, the control valve 79 moves to the lower position under the action of the spring, compressed air of the control port K enters the oil-gas separation device 80 through A to R of the control valve 79, a special pipeline for gas flowing is arranged in the oil-gas separation device, oil in the air is separated and enters the shell after the compressed air flows through the special pipeline, and clean compressed air is exhausted into the atmosphere through the exhaust pipe 81, so that the pollution to the environment is reduced.
The highest point of the hydraulic retarding braking device is provided with an exhaust valve 21, air in the shell enters an oil-gas separation device 80 through the exhaust valve 21, and compressed air subjected to oil-gas separation converges to an exhaust pipe 81 and is exhausted into the atmosphere.
(3) Principle of hydraulic-mechanical combined braking system
When the brake valve is depressed to perform mechanical braking after switching to the combined braking mode by operating the switching valve 14, the hydraulic brake also starts to be simultaneously applied when the brake valve outlet pressure reaches the set opening pressure of the pilot proportional pressure reducing valve 72. The air pressure value of the output pressure A of the pilot-controlled air proportional valve 72 and the value of the pilot oil K5 are changed in proportion within a set range, so that the compressed air at the port A flows to the port A through the port P1 of the shuttle valve 78, and the oil is proportionally input into the hydraulic working chamber 26 of the hydraulic retarder braking device through the control port K2 of the P, A oil pool 82 of the pilot valve 79, so that the hydraulic retarder braking device outputs proportional braking torque, and the mechanical and hydraulic braking linkage is automatically realized.
Fig. 6 is a schematic diagram of a cooling system integrating an engine and a hydraulic brake, wherein a hydraulic retarding brake device and a water-cooling oil heat exchanger in the hydraulic brake cooling system are designed in a split manner, the hydraulic retarding brake device and the water-cooling oil heat exchanger are connected through a hydraulic brake oil way pipeline, and a hydraulic brake working medium flows between the hydraulic retarding brake device and the hydraulic retarding brake device in a circulating manner. The circulating water pump 87 is driven by an engine, after the engine is started, the circulating water pump 87 operates, the cooling liquid in the radiator 2 flows out from a port P1, enters the engine through a port P2 of the engine 3, cools the engine, the cooled cooling liquid flows out from a port P3 of the engine 3, enters the water-cooling oil heat exchanger through a port P4 of the water-cooling oil heat exchanger 6, the high-temperature liquid working medium of the hydraulic retarding braking device 10 flows out from a port P8, flows into the heat exchanger through a hydraulic braking oil way pipeline 86 to a port P6 of the water-cooling oil heat exchanger 6, and is cooled by the cooling water entering from a port P4, and the low-temperature liquid working medium flows out from a port P7 of the water-cooling oil heat exchanger 6, flows through the hydraulic braking oil way pipeline 86 and returns to a port P9 of the hydraulic retarding braking device 10. After the cooling effect of the coolant entering the water-cooling oil heat exchanger 6 is finished, the coolant is discharged from a port P5 and reaches a port P10 of the thermostat 84 through a water pipeline 85, if the temperature of the water reaching the port P10 is lower than the set opening temperature of the thermostat 84, the thermostat 84 is not opened, the coolant is discharged from a port P12 of the thermostat 84 and enters the engine through a port P2 of the engine 3 again, the coolant is cooled in a small circulation mode, if the temperature of the water reaching the port P10 is higher than the set opening temperature of the thermostat 84, the thermostat 84 is opened, the coolant is discharged from a port P11 of the thermostat 84 and enters the radiator through a port P13 of the radiator 2, and the coolant is cooled through the radiator and then discharged from a port P1 and enters the engine through a port P2 of the engine 3 to be cooled in a large circulation mode. The radiator 2 is replenished with coolant via the expansion tank 1.
Claims (5)
1. A hydro-mechanical combined braking system for an articulated explosion-proof vehicle for a coal mine, characterized in that: comprises a hydraulic torque converter (4) connected with the rear part of an engine (3), the hydraulic torque converter (4) is connected with a gearbox (8) through an upper transmission shaft (17), the front output of the gearbox (8) is connected with a front axle (5) through a front axle transmission shaft (18), two ends of the front axle (5) are respectively connected with two wet service brakes (12), the rear output of the gearbox (8) is connected with a front connecting flange of a hydraulic retarding braking device (10) through a hinged transmission shaft (9), a rear connecting flange of the hydraulic retarding braking device (10) is connected with a rear axle (13) through a rear axle transmission shaft (11), two ends of the rear axle (13) are respectively connected with the two wet service brakes (12), two shafts of the gearbox (8) are provided with wet parking brakes (7), the hydraulic retarding braking device (10) is connected with a water-cooling oil heat exchanger (6) through a metal hose, the water-cooling oil heat exchanger (6) is connected with the radiator (2) through a water pipe, and the radiator (2) is supplemented with water through the expansion water tank (1); the four wet service brakes (12) on the front axle and the rear axle are respectively connected with a mechanical brake service brake control valve (16) and a switching valve (14) through hydraulic control pipelines, the switching valve (14) is connected with a hydraulic brake control system, and the hydraulic retarding brake device (10) is connected with an air source through a pneumatic control valve (15) and a pneumatic control pipeline.
2. The hydro-mechanical combination brake system for an articulated coal mine explosion-proof vehicle of claim 1, wherein: the hydraulic retarding brake device (10) comprises a connecting flange (20), a cover (21), a shell (22), a rotor impeller (23), a stator impeller (24), a main shaft (25), an oil storage cavity (27) and a control valve (28), wherein the cover (21) and the shell (22) form a structure in which a hydraulic working cavity (26) is arranged, the hydraulic working cavity (26) is communicated with the oil storage cavity (27), and the oil storage cavity (27) is connected with a metal hose through the control valve (28); a rotor impeller (23) and a stator impeller (24) are arranged in the hydraulic working cavity (26), the rotor impeller (23) is driven to rotate by a main shaft (25), and connecting flanges (20) are arranged at two ends of the main shaft (25).
3. The hydro-mechanical combination brake system for a coal mine articulated explosion-proof vehicle of claim 2, wherein: the wet-type service brake (12) comprises a bearing I (29), a static shell (30), a shoulder bolt (31), a disc spring group (32), a floating oil seal (33), a piston (34), an inner friction plate (35), an outer friction plate (36), a pressure plate (37), a movable shell (38), an end cover (39), a nut I (40), a bearing II (41), a screw plug (42), a shaft (43) and a nut II (44); the static shell (30) is fixedly connected with a front axle (5) or a rear axle (13) shell, a pressure plate (37) is connected with the static shell (30) through a bolt, a shaft (43) is connected and supported with a movable shell (38) through a bearing I (29) and a bearing II (41), the left end and the right end of the shaft (43) are respectively fastened through a nut I (40) and a nut II (44), an inner friction plate (35) is fixedly connected with the static shell (30) through inner teeth, an outer friction plate (36) is connected with the movable shell (38) through outer teeth and synchronously rotates with the movable shell (38), a floating oil seal (33) is arranged between the static shell (30) and the movable shell (38), the right side of the movable shell (38) is connected with an end cover (39), a screw plug (42) is arranged at the bottom of the static shell (30), the inner friction plate (35) and the outer friction plate (36) are arranged at intervals, a piston (34) is arranged at the left side of the inner friction plate (35), a, the disc spring group (32) is arranged on the shoulder bolt (31).
4. The hydro-mechanical combination brake system for an articulated coal mine explosion-proof vehicle of claim 3, wherein: the wet parking brake (7) comprises a spring shell (45), a disc spring (46), a sealing shell (47), a piston (48), an emptying nozzle assembly (49), a vent plug assembly (50), a friction plate shell (51), a powder sheet (52) and a steel sheet (53), wherein the friction plate shell (51) of the parking brake is connected with a gearbox shell, the spring shell (45) and the sealing shell (47) are connected with the friction plate shell (51) into a whole through long bolts, the disc spring (46) is arranged in a high-pressure oil cavity formed by the spring shell (45) and the sealing shell (47), the piston (48) is arranged on the right side of the disc spring (46), the right side of the piston (48) is in contact connection with the powder sheet (52), the powder sheet (52) is connected with the gearbox shaft through inner teeth and rotates along with the gearbox, the steel sheet (53) is fixedly connected with the friction plate shell (51) through outer teeth, the powder sheet (52) and the steel sheet (53) are arranged in the friction plate, an emptying nozzle assembly (49) is communicated with the high-pressure oil cavity, and a vent plug assembly (50) is communicated with the friction plate lubricating oil cavity.
5. The hydro-mechanical combination brake system for a coal mine articulated explosion-proof vehicle according to claim 1, 2, 3 or 4, wherein: the hydraulic braking control system comprises a gas storage tank (67), a safety valve (69), a knob switch valve (70), a gear control valve (71), a hydraulic control gas proportional pressure reducing valve (72), a one-way valve I (73), a one-way valve II (75), a pressure regulating valve I (74), a pressure regulating valve II (76), a shuttle valve I (77), a shuttle valve II (78), a control valve (79), a gas-oil separation device (80), an exhaust pipe (81), an exhaust valve (21), a hydraulic working cavity (26) and an oil sump (82), wherein a K port of the hydraulic control gas proportional pressure reducing valve (72) is connected with a mechanical braking control system through a mechanical independent braking switching valve (14), a P port of the hydraulic control gas proportional pressure reducing valve (72) is connected with the gas storage tank (67) through the safety valve (69), a water drainage switch (68) is arranged at the bottom of the gas storage tank (67), an A port of the hydraulic control gas proportional pressure reducing valve (72, a port P2 of a shuttle valve II (78) is connected with a port A of the shuttle valve I (77), a port P1 of the shuttle valve I (77) is connected with a pressure regulating valve I (74), the pressure regulating valve I (74) is connected with a port B of a gear control valve (71), a check valve I (73) is connected in parallel with the pressure regulating valve I (74), a port P2 of the shuttle valve I (77) is connected with a pressure regulating valve II (76), the pressure regulating valve II (76) is connected with a port A of the gear control valve (71), and a check valve II (75) is connected in parallel with the pressure regulating valve II (76); the P port of the gear control valve (71) is connected with the A port of the knob switch valve (70), and the P port of the knob switch valve (70) is connected with the air storage tank (67); an opening A of the shuttle valve II (77) is connected with an opening P and an opening K of the control valve (79), an opening A of the control valve (79) is connected with the oil pool (82), an opening R of the control valve (79) is connected with an inlet of the oil-gas separation device (80), an exhaust pipe (81) is arranged on an exhaust port of the oil-gas separation device (80), an outlet of the oil-gas separation device (80) is connected with the hydraulic working cavity (26) through an exhaust valve (21), and the hydraulic working cavity (26) is connected with the oil pool (82);
the mechanical brake control system comprises a tandem type double-loop brake valve (58), an energy accumulator I (59), an energy accumulator II (60), a liquid charging valve (61), a hydraulic pump (62), a one-way valve III (63), a parking brake valve (64) and a manual pump (65), pressure oil of the hydraulic pump (62) is divided into two paths, one path is connected with a P port of the liquid charging valve (61), and two outlets A1 and A2 of the liquid charging valve (61) are respectively connected with the energy accumulator I (59) and the energy accumulator II (60); the other path is connected with a port P of a safety valve, a port T of the safety valve is respectively connected with a fuel tank and a port T1 of a tandem type double-loop brake valve (58), a port A1 and a port A2 of the tandem type double-loop brake valve (58) are respectively connected with a front wheel service brake (56) and a rear wheel service brake (57), a port P2 of the tandem type double-loop brake valve (58) is connected with a port P of a parking brake valve (64) through a one-way valve III (63), a port A2 of the tandem type double-loop brake valve (58) is connected with a port P of a mechanical independent brake switching valve (14), the port T of the mechanical independent brake switching valve (14) is connected with the fuel tank, and the port A of the mechanical independent brake switching valve (14) is connected with a hydraulic brake control system.
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| CN112629875A (en) * | 2020-12-02 | 2021-04-09 | 中国煤炭科工集团太原研究院有限公司 | Anti-explosion rubber-tyred vehicle brake test bed for simulating long downhill |
| CN113531116A (en) * | 2021-06-12 | 2021-10-22 | 中国煤炭科工集团太原研究院有限公司 | Isolation protection device and control system based on hydraulic mechanical transmission |
| CN113958630A (en) * | 2021-09-08 | 2022-01-21 | 中国北方车辆研究所 | Mechanical hydraulic composite retarding brake device |
| CN115179917A (en) * | 2022-08-08 | 2022-10-14 | 中车大连机车研究所有限公司 | Liquid-gas combined braking control method for rail transit vehicle |
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| CN113531116A (en) * | 2021-06-12 | 2021-10-22 | 中国煤炭科工集团太原研究院有限公司 | Isolation protection device and control system based on hydraulic mechanical transmission |
| CN113531116B (en) * | 2021-06-12 | 2022-07-26 | 中国煤炭科工集团太原研究院有限公司 | Isolation protection device and control system based on hydraulic mechanical transmission |
| CN113958630A (en) * | 2021-09-08 | 2022-01-21 | 中国北方车辆研究所 | Mechanical hydraulic composite retarding brake device |
| CN113958630B (en) * | 2021-09-08 | 2024-03-08 | 中国北方车辆研究所 | Mechanical hydraulic composite retarding braking device |
| CN115179917A (en) * | 2022-08-08 | 2022-10-14 | 中车大连机车研究所有限公司 | Liquid-gas combined braking control method for rail transit vehicle |
| CN115325045A (en) * | 2022-10-18 | 2022-11-11 | 中车戚墅堰机车车辆工艺研究所有限公司 | Wet disc brake with seal clearance adjusting function |
| CN115325045B (en) * | 2022-10-18 | 2023-01-13 | 中车戚墅堰机车车辆工艺研究所有限公司 | Wet disc brake with seal clearance adjusting function |
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