CN101709725B - Downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique - Google Patents
Downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique Download PDFInfo
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Abstract
The invention discloses a downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique, comprising a pump control motor major loop, an oil supplementing loop, a heat exchange loop, a safe loop and a brake loop, wherein the pump control motor major loop is formed by combining three proportional variable pumps with small displacement in parallel and used for driving two constant displacement motors, and a roller wheel main shaft is driven to drive a hoisting machine to be lifted; the displacement of the variable pumps can be changed by detecting the rotating speed of a roller wheel by a speed sensor in real time, so that the system can be accurately controlled; the oil supplementing loop can be used for supplementing the leakage of the major loop and the oil loss when in heat exchange; the heat exchange loop comprises a hydraulic control valve, a backpressure overflow valve and a cooling device and is used for completing heat exchange work of the closed-type system; the safe loop comprises two groups of high pressure overflow valves and a one-way valve, and a protecting system is formed by the high pressure overflow valves and the one-way valve; and the brake loop can be used for realizing normal work or brake of the motor. Compared with the traditional hydraulic anti-explosion hoisting machine, by adopting the multi-pump combination technique and controlling the displacement of a main driving pump in real time according to the requirement of rotating speed, the system has good energy-saving effect, low fault rate and high control accuracy.
Description
Technical field
The present invention relates to liquid control system, relate in particular to a kind of downhole anti-explosion hoisting machine hydraulic control system that adopts multi-pump combination technique.
Background technique
Downhole anti-explosion hoisting machine is one of capital equipment of downhole anti-explosion transportation, in the mine and the engineering field do to promote, transfer personnel and material is used.At present downhole anti-explosion hoisting machine mainly contains two kinds of automatically controlled downhole anti-explosion hoisting machine and hydraulic downhole anti-explosion hoisting machines.Automatically controlled downhole anti-explosion hoisting machine main feature is the main machine structure compactness, and transportation safety is convenient, and transmission efficiency is higher; But its control panel manufacture cost is very high, costs an arm and a leg; Control panel is bulky, and maintenance is complicated; Speed regulation is limited, impacts greatly the low cruise poor-performing.Hydraulic downhole anti-explosion hoisting machine main feature is to adopt hydraulic transmission, has reduced the element that produces spark; Unloaded across-the-line starting realizes speed governing by hydraulic system fully, makes electrical control equipment simple, is convenient to explosion-proof, safe and reliable; Have stepless speed regulation, the starting commutation is steady, and low-speed running is functional, thereby is used widely.
Traditional hydraulic downhole anti-explosion hoisting machine electricity liquid speed servo control system generally is made up of proportional pressure-reducing valve, proportional cylinder, motor-driven servovalve, variable oil hydraulic cylinder, main variable displacement pump, the fixed displacement motor etc. of driving, and adopts remote hydraulic control maneuverability pattern.The driver gives one of ratio oil hydraulic cylinder input that the big flow master of system drives variable displacement pump from low to high pressure oil gradually by handling the decompression type proportional pilot valve, promote servo selector valve action, controlled variable oil hydraulic cylinder displacement and change the main inclination angle that drives the variable displacement pump swash plate and change the main flow that drives variable displacement pump, thereby change the rotating speed of oil hydraulic motor, make lift starting, accelerated service.The driver pulls different angles with the handle of decompression type proportional pilot valve, just can make the main variable displacement pump that drives export different flows, thereby make lift obtain different lifting speeies.Because be subjected to the influence of proportional pressure-reducing valve dead band and proportional cylinder frictional force, this control system is an open system, control accuracy is relatively poor, operation is insensitive, and the pivot angle of lifting speed and operating grip can not be held in proportionate relationship fully, can not realize automatic control; In addition, because system does not have oil hydraulic motor output speed feedback control system, thereby can not eliminate the oil hydraulic motor output speed error that causes owing to load variations automatically.
The main driving variable displacement pump of existing hydraulic downhole anti-explosion hoisting machine is an axial piston pump that high flow manual is operated, this pump displacement is big, can be operated in the high capacity operating mode when lift is up, but lift then can bring very big power loss to system, the energy saving of system weak effect when descending; And system can only shut down maintenance when being out of order, and reliability is low, and rate of fault is higher.
Summary of the invention
Carry task in order to overcome the problem that exists when the described hydraulic downhole anti-explosion hoisting machine of background technique is worked and to better meet downhole anti-explosion, the object of the present invention is to provide a kind of downhole anti-explosion hoisting machine hydraulic control system that adopts multi-pump combination technique, problem such as can solve preferably that the hydraulic control system energy-saving effect that present hydraulic downhole anti-explosion hoisting machine exists is poor, reliability is low, control accuracy is not high and not easy to operate.
The technical solution adopted for the present invention to solve the technical problems comprises:
The motor I, the motor II, the motor III, the motor IV, two-way proportional variable displacement pump I, two-way proportional variable displacement pump II, two-way proportional variable displacement pump III, servo selector valve I, servo selector valve II, servo selector valve III, two rod oil hydraulic cylinder I, two rod oil hydraulic cylinder II, two rod oil hydraulic cylinder III, the position transducer I, the position transducer II, the position transducer III, the proportional amplifier I, the proportional amplifier II, the proportional amplifier III, the integrating amplifier I, the integrating amplifier II, the integrating amplifier III, the one-way valve I, the one-way valve II, the one-way valve III, the one-way valve IV, one-way valve V, pressure relay, the relief valve I, the relief valve II, cooler, the adjustable restrictive valve I, the adjustable restrictive valve II, the bi-bit bi-pass solenoid directional control valve, the high-pressure overflow valve I, the high-pressure overflow valve II, the 3-position-3-way pilot operated directional control valve, the back pressure relief valve, two-way fixed displacement motor I, two-way fixed displacement motor II, disc-brake, the roller main shaft, the gear pair I, the gear pair II, depth transducer, position limit switch I, the position limit switch II, the position limit switch III, velocity transducer, the ball valve I, the ball valve II, the ball valve III, the one-way throttle valve I, the one-way throttle valve II, motor-driven selector valve, the two-position three way solenoid directional control valve, reduction valve goes out oil strainer, metering pump, the oil suction filter, fuel tank.Motor IV and metering pump are rigidly connected by coupling, the inlet port of metering pump is communicated with ball valve III oil outlet, ball valve III filler opening is communicated with oil suction filter oil outlet, oil suction filter filler opening directly connects fuel tank, the metering pump oil outlet with go out the oil strainer filler opening and be communicated with, going out the oil strainer oil outlet is communicated with one-way valve V filler opening and relief valve II filler opening respectively, one-way valve V oil outlet respectively with the reduction valve filler opening, two-position three way solenoid directional control valve filler opening, one-way valve I filler opening, one-way valve II filler opening, pressure relay filler opening and relief valve I filler opening are connected, the oil outlet of relief valve II directly connects fuel tank, two-position three way solenoid directional control valve oil outlet is communicated with motor-driven selector valve filler opening, two-position three way solenoid directional control valve return opening is communicated with adjustable restrictive valve II filler opening, adjustable restrictive valve II oil outlet directly connects fuel tank, motor-driven selector valve return opening directly connects fuel tank, motor-driven selector valve oil outlet is communicated with one-way throttle valve II filler opening, one-way throttle valve II oil outlet respectively with one-way throttle valve I filler opening, ball valve I filler opening is connected, one-way throttle valve I oil outlet is communicated with ball valve II filler opening, ball valve I oil outlet and ball valve II oil outlet are communicated with disc-brake respectively, the main shaft of roller main shaft and two-way fixed displacement motor I and two-way fixed displacement motor II is rigidly connected, the gear pair I is connected by spline with the main shaft of gear pair II with two-way fixed displacement motor II, the reduction valve oil outlet respectively with servo selector valve I, servo selector valve II, the oil inlet P mouth of servo selector valve III links to each other, the oil outlet A mouth of servo selector valve I and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder I respectively, the oil return inlet T mouth of servo selector valve I directly connects fuel tank, the piston rod of two rod oil hydraulic cylinder I links to each other with the swash plate of two-way proportional variable displacement pump I, the motor I is rigidly connected by coupling and two-way proportional variable displacement pump I, the oil outlet A mouth of servo selector valve II and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder II respectively, the oil return inlet T mouth of servo selector valve II directly connects fuel tank, the piston rod of two rod oil hydraulic cylinder II links to each other with the swash plate of two-way proportional variable displacement pump II, the motor II is rigidly connected by coupling and two-way proportional variable displacement pump II, the oil outlet A mouth of servo selector valve III and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder III respectively, the oil return inlet T mouth of servo selector valve III directly connects fuel tank, the piston rod of two rod oil hydraulic cylinder III links to each other with the swash plate of two-way proportional variable displacement pump III, the motor III is rigidly connected by coupling and two-way proportional variable displacement pump III, two-way proportional variable displacement pump I, two-way proportional variable displacement pump II, the filler opening of two-way proportional variable displacement pump III respectively with one-way valve I oil outlet, adjustable restrictive valve I filler opening, high-pressure overflow valve I filler opening, one-way valve IV oil outlet, the filler opening of pilot operated directional control valve filler opening and two-way fixed displacement motor I and two-way fixed displacement motor II is connected, two-way proportional variable displacement pump I, two-way proportional variable displacement pump II, the oil outlet of two-way proportional variable displacement pump III respectively with one-way valve II oil outlet, bi-bit bi-pass solenoid directional control valve oil outlet, one-way valve III oil outlet, high-pressure overflow valve II filler opening, the oil outlet of pilot operated directional control valve filler opening and two-way fixed displacement motor I and two-way fixed displacement motor II is connected, the pilot operated directional control valve oil outlet is communicated with back pressure relief valve filler opening, back pressure relief valve oil outlet communicates with the cooler filler opening, the cooler oil outlet directly is connected with fuel tank, relief valve I oil outlet is communicated with the cooler filler opening, adjustable restrictive valve I oil outlet is communicated with bi-bit bi-pass solenoid directional control valve filler opening, high-pressure overflow valve I oil outlet is communicated with one-way valve III filler opening, high-pressure overflow valve II oil outlet is communicated with one-way valve IV filler opening, the position transducer I is built-in to be fixedly mounted on two rod oil hydraulic cylinder I piston rods, the position transducer II is built-in to be fixedly mounted on two rod oil hydraulic cylinder II piston rods, the position transducer III is built-in to be fixedly mounted on two rod oil hydraulic cylinder III piston rods, depth transducer is installed on the gear pair II output shaft, velocity transducer is installed on the gear pair I output shaft, the proportional amplifier I, the proportional amplifier II, the proportional amplifier III is fixedly mounted in the control cabinet, the integrating amplifier I, the integrating amplifier II, the integrating amplifier III is fixedly mounted in the control cabinet.
The present invention compares with background technique, and the beneficial effect that has is:
(1) master of system drives the loop and adopts two two-way fixed displacement motors of three float amount two-way proportional variable displacement pumps combination driving in parallel, its control system is independent, requirement can drive wherein one group, two groups or three groups of master's driven pumps according to system condition, the feasible system power match, improve system works efficient, energy saving of system is effective.In addition, when fault appearred in some little pumps, system still can keep proper functioning, thereby had improved the reliability of system, and system failure rate is low, is particularly suitable for the occasion of underground work inclement condition.
(2) adopt the pump-control-motor speed control system of being with position ring, the variation of main driven pump discharge capacity is accurately controlled in the displacement that detects double-acting hydraulic cylinder in real time by position transducer, detect the rotating speed of roller main shaft in addition in real time by velocity transducer, may command master drives the variable displacement pump rate of discharge and follows load variations, by little closed loop in position and the big closed loop control of speed, improved the control accuracy of system, and not high to operator's requirement of anti-explosion hoisting machine yet, can make its fast adaptation post.
(3) compare with the conventional hydraulic anti-explosion hoisting machine, owing to saved many valve groups and pipe fitting, hydraulic system structure is simply compact, the easier reason of searching when being out of order.
Description of drawings
Accompanying drawing is a structural principle schematic representation of the present invention.
Among the figure: motor I (1a), motor II (1b), motor III (1c), motor IV (35), two-way proportional variable displacement pump I (2a), two-way proportional variable displacement pump II (2b), two-way proportional variable displacement pump III (2c), servo selector valve I (3a), servo selector valve II (3b), servo selector valve III (3c), two rod oil hydraulic cylinder I (4a), two rod oil hydraulic cylinder II (4b), two rod oil hydraulic cylinder III (4c), position transducer I (5a), position transducer II (5b), position transducer III (5c), proportional amplifier I (6a), proportional amplifier II (6b), proportional amplifier III (6c), integrating amplifier I (7a), integrating amplifier II (7b), integrating amplifier III (7c), one-way valve I (8a), one-way valve II (8b), one-way valve III (15a), one-way valve IV (15b), one-way valve V (31), pressure relay (9), relief valve I (10), relief valve II (32), cooler (11), adjustable restrictive valve I (12), adjustable restrictive valve II (29), bi-bit bi-pass solenoid directional control valve (13), high-pressure overflow valve I (14a), high-pressure overflow valve II (14b), 3-position-3-way pilot operated directional control valve (16), back pressure relief valve (17), two-way fixed displacement motor I (18a), two-way fixed displacement motor II (18b), disc-brake (19), roller main shaft (20), gear pair I (21a), gear pair II (21b), depth transducer (22), position limit switch I (23a), position limit switch II (23b), position limit switch III (23c), velocity transducer (24), ball valve I (25a), ball valve II (25b), ball valve III (25c), one-way throttle valve I (26a), one-way throttle valve II (26b), motor-driven selector valve (27), two-position three way solenoid directional control valve (28), reduction valve (30), refill formula filter (33), unidirectional metering pump (34), strainer (36), fuel tank (37).
Embodiment
The invention will be further described below in conjunction with drawings and Examples:
As shown in drawings, motor 35 among the present invention and metering pump 34 are rigidly connected by coupling, the inlet port of metering pump 34 is communicated with ball valve 25c oil outlet, ball valve 25c filler opening is communicated with oil suction filter 36 oil outlets, oil suction filter 36 filler openings directly connect fuel tank 37, metering pump 34 oil outlets with go out oil strainer 33 filler openings and be communicated with, going out oil strainer 33 oil outlets is communicated with one-way valve 31 filler openings and relief valve 32 filler openings respectively, one-way valve 31 oil outlets respectively with reduction valve 30 filler openings, two-position three way solenoid directional control valve 28 filler openings, one-way valve 8a filler opening, one-way valve 8b filler opening, pressure relay 9 filler openings and relief valve 10 filler openings are connected, the oil outlet of relief valve 32 directly connects fuel tank 37, two-position three way solenoid directional control valve 28 oil outlets are communicated with motor-driven selector valve 27 filler openings, two-position three way solenoid directional control valve 28 return openings are communicated with adjustable restrictive valve 29 filler openings, adjustable restrictive valve 29 oil outlets directly connect fuel tank 37, motor-driven selector valve 27 return openings directly connect fuel tank 37, motor-driven selector valve 27 oil outlets are communicated with one-way throttle valve 26b filler opening, one-way throttle valve 26b oil outlet respectively with one-way throttle valve 26a filler opening, ball valve 25a filler opening is connected, one-way throttle valve 26a oil outlet is communicated with ball valve 25b filler opening, ball valve 25a oil outlet and ball valve 25b oil outlet are communicated with disc-brake 19 respectively, roller main shaft 20 is rigidly connected with the main shaft of two-way fixed displacement motor 18a and two-way fixed displacement motor 18b, and gear pair 21a is connected by spline with the main shaft of two-way fixed displacement motor 18b with gear pair 21b.Reduction valve 30 oil outlets respectively with servo selector valve 3a, servo selector valve 3b, the oil inlet P mouth of servo selector valve 3c links to each other, the oil outlet A mouth of servo selector valve 3a and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder 4a respectively, the oil return inlet T mouth of servo selector valve 3a directly connects fuel tank 37, the piston rod of two rod oil hydraulic cylinder 4a links to each other with the swash plate of two-way proportional variable displacement pump 2a, motor 1a is rigidly connected by coupling and two-way proportional variable displacement pump 2a, the oil outlet A mouth of servo selector valve 3b and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder 4b respectively, the oil return inlet T mouth of servo selector valve 3b directly connects fuel tank 37, the piston rod of two rod oil hydraulic cylinder 4b links to each other with the swash plate of two-way proportional variable displacement pump 2b, motor 1b is rigidly connected by coupling and two-way proportional variable displacement pump 2b, the oil outlet A mouth of servo selector valve 3c and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder 4c respectively, the oil return inlet T mouth of servo selector valve 3c directly connects fuel tank 37, the piston rod of two rod oil hydraulic cylinder 4c links to each other with the swash plate of two-way proportional variable displacement pump 2c, motor 1c is rigidly connected by coupling and two-way proportional variable displacement pump 2c, two-way proportional variable displacement pump 2a, two-way proportional variable displacement pump 2b, the filler opening of two-way proportional variable displacement pump 2c respectively with one-way valve 8a oil outlet, adjustable restrictive valve 12 filler openings, high-pressure overflow valve 14a filler opening, one-way valve 15b oil outlet, the filler opening of pilot operated directional control valve 16 filler openings and two-way fixed displacement motor 18a and two-way fixed displacement motor 18b is connected, two-way proportional variable displacement pump 2a, two-way proportional variable displacement pump 2b, the oil outlet of two-way proportional variable displacement pump 2c respectively with one-way valve 8b oil outlet, bi-bit bi-pass solenoid directional control valve 13 oil outlets, one-way valve 15a oil outlet, high-pressure overflow valve 14b filler opening, the oil outlet of pilot operated directional control valve 16 filler openings and two-way fixed displacement motor 18a and two-way fixed displacement motor 18b is connected, pilot operated directional control valve 16 oil outlets are communicated with back pressure relief valve 17 filler openings, back pressure relief valve 17 oil outlets communicate with cooler 11 filler openings, cooler 11 oil outlets directly are connected with fuel tank 37, relief valve 10 oil outlets are communicated with cooler 11 filler openings, adjustable restrictive valve 12 oil outlets are communicated with bi-bit bi-pass solenoid directional control valve 13 filler openings, high-pressure overflow valve 14a oil outlet is communicated with one-way valve 15a filler opening, and high-pressure overflow valve 14b oil outlet is communicated with one-way valve 15b filler opening.Position transducer 5a is built-in to be fixedly mounted on two rod oil hydraulic cylinder 4a piston rods, position transducer 5b is built-in to be fixedly mounted on two rod oil hydraulic cylinder 4b piston rods, position transducer 5c is built-in to be fixedly mounted on two rod oil hydraulic cylinder 4c piston rods, depth transducer 22 is installed on the gear pair 21b output shaft, velocity transducer 24 is installed on the gear pair 21a output shaft, proportional amplifier 6a, proportional amplifier 6b, proportional amplifier 6c are fixedly mounted in the control cabinet, and integrating amplifier 7a, integrating amplifier 7b, integrating amplifier 7c are fixedly mounted in the control cabinet.
Working principle of the present invention is as follows:
During system works, three float amount rate variable parallel connection of pumps combinations drive, and its control system is independent, can require driving one group, two groups or three groups of master's driven pumps wherein according to system condition.With first group of master's drive system is example, motor 1a drags two-way proportional variable displacement pump 2a and rotates, servo selector valve 3a and two rod oil hydraulic cylinder 4a, position transducer 5a, proportional amplifier 6a, integrating amplifier 7a have formed the Variable Control mechanism of two-way proportional variable displacement pump, can accurately control the discharge capacity of two-way proportional variable displacement pump 2a according to the real-time detected displacement amount of position transducer 5a, guarantee the system stability fuel feeding.The fluid of unidirectional metering pump 34 outputs is transported to the oil inlet P mouth of servo selector valve 3a through reduction valve 30, by the moving direction that dead electricity changes two rod oil hydraulic cylinder 4a that gets of servo selector valve 3a proportion electro-magnet, thereby drive two-way proportional variable displacement pump 2a clockwise and anticlockwise.By velocity transducer 24 detected roller main shaft 20 tach signals, after integrating amplifier 7a computing, the signal difference of output is controlled the proportion electro-magnet at servo selector valve 3a two ends, and then control the aperture of servo selector valve 3a spool, drive two rod oil hydraulic cylinder 4a piston rod proportional motion, drive two-way proportional variable displacement pump 2a swashplate angle ratio and change, form the big closed loop control of speed according to roller main shaft 20 rotating speed real-time change.When depth indicator 22 stroke collision blocks were met deceleration point position limit switch 23b, operator reduced the potentiometer voltage setting value U on the control panel
g, Hoist Speed is slowed down; Meet halt position limit switch 23a when depth indicator 22 stroke collision blocks, operator press the stop button on the control panel, make lift stop lifting.By the little closed loop in position and these two closed loop control systems of the big closed loop of speed, can improve control accuracy according to the accurate control ratio variable of roller spindle speed pump delivery, avoided the dead band influence of traditional proportional pressure-reducing valve; Realized power adaptive in addition, energy saving of system is effective.
The security of system loop is made up of forward and reverse each high-pressure overflow valve 14a of one group and one-way valve 15a combination, high-pressure overflow valve 14b and one-way valve 15b.Cause that system oil pressure is too high and when surpassing preset pressure when load is excessive, high-pressure overflow valve 14a or high-pressure overflow valve 14b action, the overflow of major loop high side to low side damages system in order to avoid oil pressure is too high.Adjustable restrictive valve 12 and bi-bit bi-pass solenoid directional control valve 13 are used for that lift stops or when braking; be communicated with height pressure side pipeline; discharge the peak value high pressure in the major loop, protection two-way proportional variable displacement pump 2a, two-way proportional variable displacement pump 2b, two-way proportional variable displacement pump 2c and two-way fixed displacement motor 18a, two-way fixed displacement motor 18b.
System's feed circuit by oil suction filter 36, ball valve 25c, metering pump 34, motor 35, go out oil strainer 33, one-way valve 31, one-way valve 8a, one-way valve 8b, pressure relay 9 and relief valve 10 formed.The makeup oil of unidirectional metering pump 34 outputs because of its oil pressure is lower than major loop high pressure side oil pressure, and is higher than the low voltage side oil pressure, so through one-way valve 8a or 8b input major loop low voltage side, to replenish the fluid that main system runs off because of heat exchange and leakage, finish repairing work.Be provided with pressure relay 9 in feed circuit, in order to guarantee certain oil compensation pressure, if oil compensation pressure is lower than setting value, pressure relay 9 disconnects, and electric control circuit makes system motor 1a, motor 1b, motor 1c outage, and system quits work.Also be provided with relief valve 10 in this loop, be used for controlling oil compensation pressure, make unnecessary fluid flow back to fuel tank 37 through cooler 11.
System's heat exchange loop is made up of pilot operated directional control valve 16, back pressure relief valve 17 and cooler 11.Controlled by high and low pressure side oil pressure, pilot operated directional control valve 16 makes the major loop low voltage side be communicated with back pressure relief valve 17, and major loop mesolow side fluid is opened back pressure relief valve 17, flows back to fuel tank 37 by cooler 11, finishes heat exchange work.Back pressure relief valve 17 set pressures define major loop mesolow side pressure, i.e. back pressure pressure.
System's brake circuit by oil suction filter 36, ball valve 25a, ball valve 25b, ball valve 25c, metering pump 34, go out oil strainer 33, one-way valve 31, two-position three way solenoid directional control valve 28, adjustable restrictive valve 29, motor-driven selector valve 27, one-way throttle valve 26a, one-way throttle valve 26b and disc-brake 19 and form.
During normal the driving, motor-driven selector valve 27 is failure to actuate, two-position three way solenoid directional control valve 28 right-hand member electromagnet get electric work, bi-bit bi-pass solenoid directional control valve 13 right-hand members get electric work, by the pressure oil of metering pump 34 output through going out the two ends that oil strainer 33, one-way valve 31, two-position three way solenoid directional control valve 28, motor-driven selector valve 27, one-way throttle valve 26a and one-way throttle valve 26b arrive disc-brake 19 respectively, disc-brake 19 is opened, and lift is started working.One-way throttle valve 26a makes disc-brake delay work, to coordinate instantaneous downslide when preventing heavy load starting building-up time mutually with major loop pressure.
During orderly shutdown, operator press stop button, bi-bit bi-pass solenoid directional control valve 13 and two-position three way solenoid directional control valve 28 dead electricity, fluid in the disc-brake 19 is through throttle valve 26a, motor-driven selector valve 27, two-position three way solenoid directional control valve 28, adjustable restrictive valve 29 oil sump tanks 37, disc-brake 19 brake sticking brakes.One-way throttle valve 26b makes disc-brake 19 delay braking, can reduce braking and impact, and realizes the two-stage braking.
When the power supply sudden power caused improper braking, the fluid in the disc-brake 19 was through throttle valve 26a, 26b, motor-driven selector valve 27, two-position three way solenoid directional control valve 28, adjustable restrictive valve 29 oil sump tanks 37, disc-brake 19 brake sticking brakes.Set its braking deceleration by the amount of restriction of adjusting adjustable restrictive valve 29, realize the orientation braking.
When lift meets accident, foot-operated motor-driven selector valve 27, on the one hand, position limit switch 23c action, bi-bit bi-pass solenoid directional control valve 13 outage returns, disc-brake 19 oil return brake sticking brakes; On the other hand, motor-driven selector valve 27 oil return side conductings realize disc-brake oil return braking.
Claims (3)
1. downhole anti-explosion hoisting machine hydraulic control system that adopts multi-pump combination technique, it is characterized in that comprising: motor I (1a), motor II (1b), motor III (1c), motor IV (35), two-way proportional variable displacement pump I (2a), two-way proportional variable displacement pump II (2b), two-way proportional variable displacement pump III (2c), servo selector valve I (3a), servo selector valve II (3b), servo selector valve III (3c), two rod oil hydraulic cylinder I (4a), two rod oil hydraulic cylinder II (4b), two rod oil hydraulic cylinder III (4c), position transducer I (5a), position transducer II (5b), position transducer III (5c), proportional amplifier I (6a), proportional amplifier II (6b), proportional amplifier III (6c), integrating amplifier I (7a), integrating amplifier II (7b), integrating amplifier III (7c), one-way valve I (8a), one-way valve II (8b), one-way valve III (15a), one-way valve IV (15b), one-way valve V (31), pressure relay (9), relief valve I (10), relief valve II (32), cooler (11), adjustable restrictive valve I (12), adjustable restrictive valve II (29), bi-bit bi-pass solenoid directional control valve (13), high-pressure overflow valve I (14a), high-pressure overflow valve II (14b), 3-position-3-way pilot operated directional control valve (16), back pressure relief valve (17), two-way fixed displacement motor I (18a), two-way fixed displacement motor II (18b), disc-brake (19), roller main shaft (20), gear pair I (21a), gear pair II (21b), depth transducer (22), position limit switch I (23a), position limit switch II (23b), position limit switch III (23c), velocity transducer (24), ball valve I (25a), ball valve II (25b), ball valve III (25c), one-way throttle valve I (26a), one-way throttle valve II (26b), motor-driven selector valve (27), two-position three way solenoid directional control valve (28), reduction valve (30), go out oil strainer (33), metering pump (34), oil suction filter (36), fuel tank (37), motor IV (35) is rigidly connected by coupling with metering pump (34), the inlet port of metering pump (34) is communicated with ball valve III (25c) oil outlet, ball valve III (25c) filler opening is communicated with oil suction filter (36) oil outlet, oil suction filter (36) filler opening directly connects fuel tank (37), metering pump (34) oil outlet with go out oil strainer (33) filler opening and be communicated with, going out oil strainer (33) oil outlet is communicated with one-way valve V (31) filler opening and relief valve II (32) filler opening respectively, one-way valve V (31) oil outlet respectively with reduction valve (30) filler opening, two-position three way solenoid directional control valve (28) filler opening, one-way valve I (8a) filler opening, one-way valve II (8b) filler opening, pressure relay (9) filler opening and relief valve I (10) filler opening are connected, the oil outlet of relief valve II (32) directly connects fuel tank (37), two-position three way solenoid directional control valve (28) oil outlet is communicated with motor-driven selector valve (27) filler opening, two-position three way solenoid directional control valve (28) return opening is communicated with adjustable restrictive valve II (29) filler opening, adjustable restrictive valve II (29) oil outlet directly connects fuel tank (37), motor-driven selector valve (27) return opening directly connects fuel tank (37), motor-driven selector valve (27) oil outlet is communicated with one-way throttle valve II (26b) filler opening, one-way throttle valve II (26b) oil outlet respectively with one-way throttle valve I (26a) filler opening, ball valve I (25a) filler opening is connected, one-way throttle valve I (26a) oil outlet is communicated with ball valve II (25b) filler opening, ball valve I (25a) oil outlet and ball valve II (25b) oil outlet are communicated with disc-brake (19) respectively, roller main shaft (20) is rigidly connected with the main shaft of two-way fixed displacement motor I (18a) and two-way fixed displacement motor II (18b), and gear pair I (21a) is connected by spline with the main shaft of gear pair II (21b) with two-way fixed displacement motor II (18b).
2. according to right 1 described a kind of downhole anti-explosion hoisting machine hydraulic control system that adopts multi-pump combination technique, it is characterized in that: reduction valve (30) oil outlet respectively with servo selector valve I (3a), servo selector valve II (3b), the oil inlet P mouth of servo selector valve III (3c) links to each other, the oil outlet A mouth of servo selector valve I (3a) and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder I (4a) respectively, the oil return inlet T mouth of servo selector valve I (3a) directly connects fuel tank (37), the piston rod of two rod oil hydraulic cylinder I (4a) links to each other with the swash plate of two-way proportional variable displacement pump I (2a), motor I (1a) is rigidly connected by coupling and two-way proportional variable displacement pump I (2a), the oil outlet A mouth of servo selector valve II (3b) and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder II (4b) respectively, the oil return inlet T mouth of servo selector valve II (3b) directly connects fuel tank (37), the piston rod of two rod oil hydraulic cylinder II (4b) links to each other with the swash plate of two-way proportional variable displacement pump II (2b), motor II (1b) is rigidly connected by coupling and two-way proportional variable displacement pump II (2b), the oil outlet A mouth of servo selector valve III (3c) and B mouth are connected with the oil inlet and outlet of two rod oil hydraulic cylinder III (4c) respectively, the oil return inlet T mouth of servo selector valve III (3c) directly connects fuel tank (37), the piston rod of two rod oil hydraulic cylinder III (4c) links to each other with the swash plate of two-way proportional variable displacement pump III (2c), motor III (1c) is rigidly connected by coupling and two-way proportional variable displacement pump III (2c), two-way proportional variable displacement pump I (2a), two-way proportional variable displacement pump II (2b), the filler opening of two-way proportional variable displacement pump III (2c) respectively with one-way valve I (8a) oil outlet, adjustable restrictive valve I (12) filler opening, high-pressure overflow valve I (14a) filler opening, one-way valve IV (15b) oil outlet, the filler opening of pilot operated directional control valve (16) filler opening and two-way fixed displacement motor I (18a) and two-way fixed displacement motor II (18b) is connected, two-way proportional variable displacement pump I (2a), two-way proportional variable displacement pump II (2b), the oil outlet of two-way proportional variable displacement pump III (2c) respectively with one-way valve II (8b) oil outlet, bi-bit bi-pass solenoid directional control valve (13) oil outlet, one-way valve III (15a) oil outlet, high-pressure overflow valve II (14b) filler opening, the oil outlet of pilot operated directional control valve (16) filler opening and two-way fixed displacement motor I (18a) and two-way fixed displacement motor II (18b) is connected, pilot operated directional control valve (16) oil outlet is communicated with back pressure relief valve (17) filler opening, back pressure relief valve (17) oil outlet communicates with cooler (11) filler opening, cooler (11) oil outlet directly is connected with fuel tank (37), relief valve I (10) oil outlet is communicated with cooler (11) filler opening, adjustable restrictive valve I (12) oil outlet is communicated with bi-bit bi-pass solenoid directional control valve (13) filler opening, high-pressure overflow valve I (14a) oil outlet is communicated with one-way valve III (15a) filler opening, and high-pressure overflow valve II (14b) oil outlet is communicated with one-way valve IV (15b) filler opening.
3. according to right 1 described a kind of downhole anti-explosion hoisting machine hydraulic control system that adopts multi-pump combination technique, it is characterized in that: position transducer I (5a) is built-in to be fixedly mounted on two rod oil hydraulic cylinder I (4a) piston rods, position transducer II (5b) is built-in to be fixedly mounted on two rod oil hydraulic cylinder II (4b) piston rods, position transducer III (5c) is built-in to be fixedly mounted on two rod oil hydraulic cylinder III (4c) piston rods, depth transducer (22) is installed on gear pair II (21b) output shaft, velocity transducer (24) is installed on gear pair I (21a) output shaft, proportional amplifier I (6a), proportional amplifier II (6b), proportional amplifier III (6c) is fixedly mounted in the control cabinet, integrating amplifier I (7a), integrating amplifier II (7b), integrating amplifier III (7c) is fixedly mounted in the control cabinet.
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| CN2009101865008A CN101709725B (en) | 2009-11-17 | 2009-11-17 | Downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique |
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| CN2009101865008A CN101709725B (en) | 2009-11-17 | 2009-11-17 | Downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique |
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