CN203486777U - Single-rail crane hydraulic control device - Google Patents
Single-rail crane hydraulic control device Download PDFInfo
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- CN203486777U CN203486777U CN201320583231.0U CN201320583231U CN203486777U CN 203486777 U CN203486777 U CN 203486777U CN 201320583231 U CN201320583231 U CN 201320583231U CN 203486777 U CN203486777 U CN 203486777U
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Abstract
The utility model discloses a single-rail crane hydraulic control device, relates to a convey device used in a mine laneway and aims to provide the single-rail crane hydraulic control device which is space-saving, efficient and safe. A hydraulic system of the single-rail crane hydraulic control device comprises a main system, a control system and an auxiliary system, wherein the main system comprises a plurality of hydraulic motors and an axial plunger variable pump; the control system comprises a plurality of hydraulic valves and an oil replenishing valve; the auxiliary system comprises a brake pump and a plurality of hydraulic valves; the single-rail crane hydraulic control device comprises a walking loop, a clamping loop, a brake and direction controlling loop, a starting loop, an accelerator control loop, a crane beam work loop and a boosting loop.
Description
Technical field
The utility model relates to a kind of conveying arrangement, particularly relates to a kind of monorail crane locomotive hydraulic control device for drive transportation.
Background technology
Along with the application of new science and technology at coal industry field, the construction of safety, highly efficient and productive Modern Pit, the up-to-dateness of assistant conveyance becomes the important indicator of weighing the modern level in a colliery, and the efficiency of assistant conveyance directly affects mine production efficiency simultaneously.Therefore the assistant conveyance mode that develops efficient quick is a vital task of China's coal-mine industrial construction.As the monorail crane Stady On The Auxiliary Transportation Systems of one of high-yield and high-efficiency assistant conveyance, more and more demonstrate its advantage, it is not subject to the impact of base plate condition, and belt heading arrangement convenience is saved space, and conveying efficiency is high.The fully mechanized coal face removal of home work of falling face that past one month just can complete, utilizes monorail crane locomotive hydraulic control device in one week, to complete, and has greatly improved the efficiency of assistant conveyance, thereby has improved full efficiency.
Utility model content
The technical problems to be solved in the utility model is to provide a kind of space, efficient, safe monorail crane locomotive hydraulic control device saved.
The utility model monorail crane locomotive hydraulic control device, comprise walking loop, Clamping Circuit, braking and direction control circuit, start loop, Throttle Opening Control loop and lifting beam work loop, wherein said walking loop comprises diesel motor, two way variable displacement pump, slippage pump, stroking mechanism, DA control cock, pressure shut-off valve and several HM Hydraulic Motor, described diesel motor is used for driving two way variable displacement pump and slippage pump to produce high pressure oil, the actuator port of the HM Hydraulic Motor that two actuator ports of described two way variable displacement pump are in parallel with several is connected, the swash plate of two way variable displacement pump is controlled by stroking mechanism, two actuator ports of described stroking mechanism are connected respectively at two actuator ports of three position four-way directional control valve, the oil inlet P of described three position four-way directional control valve is connected with the oil outlet of slippage pump by DA control cock, the oil inlet of described pressure shut-off valve is connected with the oil inlet P of three position four-way directional control valve, the startup control port of pressure shut-off valve is connected with two actuator ports of two way variable displacement pump by shuttle valve, the oil outlet of described slippage pump is connected with the oil inlet of low pressure relief valve,
Braking and direction control circuit comprise quantitative gear pump, the first board-like ball valve, the first shuttle valve, the first two four-way pilot operated directional control valves, the second two four-way pilot operated directional control valves, brake cylinder, the first electro-hydraulic reversing valve and the second electro-hydraulic reversing valve, described quantitative gear pump passes through diesel engine drives, the oil outlet of quantitative gear pump simultaneously with the first two four-way pilot operated directional control valves, the second two four-way pilot operated directional control valves, the oil inlet P of the first electro-hydraulic reversing valve and the second electro-hydraulic reversing valve is connected, two actuator ports of described the first electro-hydraulic reversing valve are connected with two hydraulic control hydraulic fluid ports of the first two four-way pilot operated directional control valves respectively, two actuator ports of described the second electro-hydraulic reversing valve are connected with two hydraulic control hydraulic fluid ports of three position four-way directional control valve, by the first shuttle valve, be connected with the left side hydraulic control hydraulic fluid port of the second two four-way pilot operated directional control valves simultaneously, one of them actuator port of one of them actuator port of described the first two four-way pilot operated directional control valves and the second two four-way pilot operated directional control valves is connected with the import of the first board-like ball valve, the outlet of described the first board-like ball valve is connected with the rod chamber of some brake cylinders, in the rodless cavity of described brake cylinder, pressure spring is installed,
Clamping Circuit comprises the second check valve, the 3rd check valve, pressure sensor, little hydraulic accumulator, the first by pass valve, clamping oil cylinder and two cover pressure tester, two actuator ports of two way variable displacement pump are connected with several clamping oil cylinders by the second check valve and the 3rd check valve respectively, in loop, be connected with pressure sensor, little hydraulic accumulator and the first by pass valve, two cover pressure tester are connected on respectively the oil inlet place of clamping oil cylinder;
Start loop and comprise hydraulic hand-pump, large hydraulic accumulator, pressure stop valve, the second by pass valve, the first two-position four-way hand valve, primer fluid pressure motor, the second board-like ball valve, the 4th check valve and the 5th check valve, the oil outlet of hydraulic hand-pump is connected with the oil inlet P of the first two-position four-way hand valve by the second board-like ball valve, one of them actuator port of described the first two-position four-way hand valve is connected with the oil inlet of primer fluid pressure motor, described large hydraulic accumulator and the second by pass valve are connected between hydraulic hand-pump and the second board-like ball valve, the oil outlet of described quantitative gear pump is entering by the 4th check valve and the 5th check valve and the second board-like ball valve respectively, oil outlet is connected, the oil inlet of described pressure stop valve is connected with the oil outlet of quantitative gear pump,
Throttle Opening Control loop comprises two tubular ball valves, two Remote control valves, the second shuttle valve and hydraulic throttle actuators, the oil outlet of described quantitative gear pump is connected with the oil inlet of two Remote control valves by two tubular ball valves respectively, and the oil outlet of two described Remote control valves is connected with hydraulic throttle actuator by the second shuttle valve;
Lifting beam work loop comprises low pressure ball valve, the second two-position four-way hand valve, the 6th check valve, the 3rd by pass valve, the 7th check valve and four quick couplings, the oil outlet of quantitative gear pump is connected with the oil inlet P of the second two-position four-way hand valve by the 6th check valve, one of them actuator port of described the second two-position four-way hand valve is connected with two quick couplings wherein by the 7th check valve, two other quick coupling is connected with fuel tank, and described the 3rd by pass valve is connected between the 6th check valve and the second two-position four-way hand valve.
The utility model monorail crane locomotive hydraulic control device, wherein said walking loop also comprises high-pressure overflow valve and flushing and Fill valve, the oil inlet of two described high-pressure overflow valves is connected with the actuator port of two way variable displacement pump respectively, described flushing is connected with the actuator port of two way variable displacement pump respectively with two actuator ports of Fill valve, rinses and is connected with fuel tank with the return opening of Fill valve.
The utility model monorail crane locomotive hydraulic control device, wherein said walking loop also comprises two six-way transfer valves, the described HM Hydraulic Motor of part is connected on two actuator ports of two way variable displacement pump by two six-way transfer valves.
The utility model monorail crane locomotive hydraulic control device, also comprise boost-up circuit, described boost-up circuit comprises pressure charging valve and stacked compression release valve, the oil inlet of described stacked compression release valve is connected with the oil outlet of the first board-like ball valve, the oil outlet of stacked compression release valve is connected with the oil inlet of pressure charging valve, and the oil outlet of described pressure charging valve is connected with the oil inlet of clamping oil cylinder.
The utility model monorail crane locomotive hydraulic control device, is connected with level sensor, air filter, liquid level liquid thermometer and temperature sensor on wherein said fuel tank, between fuel tank and system, be connected with radiator.
The utility model monorail crane locomotive hydraulic control device difference from prior art is that the utility model monorail crane locomotive hydraulic control device is provided with a plurality of Hydraulic Pumps and HM Hydraulic Motor, can provide enough power for each loop, add that the Clamping Circuit and the boost-up circuit that are provided with are system supercharging, effectively guarantee the normal work of system, improved conveying efficiency; The braking being provided with and direction control circuit make service braking and emergency braking separate, guaranteed the brake safe of system; In hydraulic circuit, in parallel a plurality of by pass valves and reducing valve, avoid meeting accident because oil pressure in oil circuit is too high, improved the safety of system; The design of single track also makes this device can in narrow drive, save more space.
Below in conjunction with accompanying drawing, monorail crane locomotive hydraulic control device of the present utility model is described further.
Accompanying drawing explanation
Fig. 1 is the hydraulic schematic diagram of the utility model monorail crane locomotive hydraulic control device;
Fig. 2 is the hydraulic schematic diagram in loop of walking in the utility model monorail crane locomotive hydraulic control device;
Fig. 3 is braking and direction control circuit hydraulic schematic diagram in the utility model monorail crane locomotive hydraulic control device.
Fig. 4 is Clamping Circuit hydraulic schematic diagram in the utility model monorail crane locomotive hydraulic control device;
Fig. 5 starts loop hydraulic schematic diagram in the utility model monorail crane locomotive hydraulic control device;
Fig. 6 is Throttle Opening Control loop hydraulic schematic diagram in the utility model monorail crane locomotive hydraulic control device;
Fig. 7 is lifting beam work loop hydraulic schematic diagram in the utility model monorail crane locomotive hydraulic control device;
Fig. 8 is boost-up circuit hydraulic schematic diagram in the utility model monorail crane locomotive hydraulic control device.
The specific embodiment
As shown in Figure 1, the utility model monorail crane locomotive hydraulic control device comprises walking loop, braking and direction control circuit, Clamping Circuit, startup loop, Throttle Opening Control loop, lifting beam work loop and boost-up circuit.
Shown in Fig. 2, walking loop comprises diesel motor 3, two way variable displacement pump 1, slippage pump 53, stroking mechanism 54, DA control cock 56, pressure shut-off valve 68, high-pressure overflow valve 55, flushing and Fill valve 69 and 12 HM Hydraulic Motor 6, diesel motor 3 is for driving two way variable displacement pump 1 and slippage pump 53 to produce high pressure oil, the actuator port of the HM Hydraulic Motor 6 that two actuator ports of two way variable displacement pump 1 are in parallel with 12 is connected, and wherein 4 HM Hydraulic Motor 6 are connected on two actuator ports of two way variable displacement pump 1 by two six-way transfer valves 7.The swash plate of two way variable displacement pump 1 is controlled by stroking mechanism 54, two actuator ports of stroking mechanism 54 are connected respectively at two actuator ports of three position four-way directional control valve 57, the oil inlet P of three position four-way directional control valve 57 is connected with the oil outlet of slippage pump 53 by DA control cock 56, the oil inlet of pressure shut-off valve 68 is connected with the oil inlet P of three position four-way directional control valve 57, the startup control port of pressure shut-off valve 68 is connected with two actuator ports of two way variable displacement pump 1 by shuttle valve, and the oil outlet of slippage pump 53 is connected with the oil inlet of low pressure relief valve 67; The oil inlet of two high-pressure overflow valves 68 is connected with the actuator port of two way variable displacement pump 1 respectively, rinses and is connected with the actuator port of two way variable displacement pump 1 respectively with two actuator ports of Fill valve 69, rinses and is connected with fuel tank with the return opening of Fill valve 69.
The working process in walking loop: drive two way variable displacement pump 1 and slippage pump 53 to produce pressure oil by diesel motor 3, the high pressure oil that wherein two way variable displacement pump 1 produces directly enters HM Hydraulic Motor 6, HM Hydraulic Motor 6 drives the drive wheel on monorail crane locomotive to rotate and makes monorail crane locomotive walking, and stroking mechanism 54 is realized the rotating speed of HM Hydraulic Motor 6 and the control turning to by controlling the swash plate of two way variable displacement pump 1.The low pressure oil flowing out from slippage pump 53 arrives the P mouth of three position four-way directional control valve 57 stroking mechanism through DA control cock 56, DA control cock claims again Speed sensing control cock, it is according to the uninterrupted at valve inlet place, output is proportional control presssure with it, the variable control mechanism of control presssure and two way variable displacement pump 1 connects together, just form DA and controlled closed fhdraulic system, this system can be carried out power division automatically, and DA control cock 56 can make a part of fuel feeding of slippage pump 53 be converted into pilot pressure by the difference of engine speed.Pressure shut-off valve 68 is equivalent to a kind of pressure adjusting function, when system pressure reaches pressure limit value, pressure shut-off valve 68 is opened rapidly, and control presssure reduces and then promotion two way variable displacement pump 1 swash plate reduces capacity of pump to minimum, to reach the effect of restriction system pressure to meta motion.For the situation that has instantaneous variation load; high-pressure overflow valve 55 works and realizes system overvoltage protection; the high 30bar of high-pressure overflow valve 55 setting value specific pressure shutoff valve 68 pressure set points, it only opens in short-term when pressure peak appears in system moment, makes system overflow heating minimum.When running gear is normally worked, another chamber low pressure of HM Hydraulic Motor 6 one chamber high pressure, the pressure of high pressure chest side is controlled oil promotion flushing and is moved and open with Fill valve 69 spools, and the fluid of low pressure side flows back to cooling vessel or fuel tank through flush valve and by pass valve, and the deep fat in closed system is carried out to circulating cooling.
Shown in Fig. 3, braking and direction control circuit comprise the board-like ball valve of quantitative gear pump 2, first 58, the first shuttle valve 59, the first two four-way pilot operated directional control valves 8, the second two four-way pilot operated directional control valves 45, brake cylinder 26, the first electro-hydraulic reversing valve 24 and the second electro-hydraulic reversing valves 46.Quantitative gear pump 2 drives by diesel motor 3, the oil outlet of quantitative gear pump 2 simultaneously with the first two four-way pilot operated directional control valves 8, the second two four-way pilot operated directional control valves 45, the oil inlet P of the first electro-hydraulic reversing valve 24 and the second electro-hydraulic reversing valve 46 is connected, two actuator ports of the first electro-hydraulic reversing valve 24 are connected with two hydraulic control hydraulic fluid ports of the first two four-way pilot operated directional control valves 8 respectively, two actuator ports of the second electro-hydraulic reversing valve 46 are connected with two hydraulic control hydraulic fluid ports of three position four-way directional control valve 57, by the first shuttle valve 59, be connected with the left side hydraulic control hydraulic fluid port of the second two four-way pilot operated directional control valves 45 simultaneously, one of them actuator port of one of them actuator port of the first two four-way pilot operated directional control valves 8 and the second two four-way pilot operated directional control valves 45 is connected with the import of the first board-like ball valve 58, the outlet of the first board-like ball valve 58 is connected with the rod chamber of some brake cylinders 26, in the rodless cavity of brake cylinder 26, pressure spring is installed.
The working process of braking and direction control circuit: by controlling the second electro-hydraulic reversing valve 46 commutations, one of them actuator port of the second electro-hydraulic reversing valve 46 is communicated with the oil outlet of quantitative gear pump 2, this actuator port is controlled the second two four-way pilot operated directional control valve 45 commutations by the first shuttle valve 59, the actuator port B of the second two four-way pilot operated directional control valves 45 is also communicated with the oil outlet of quantitative gear pump 2, if open the first board-like ball valve 58, the pressure oil of quantitative gear pump 2 enters in the rod chamber of brake cylinder 26 by the second two four-way pilot operated directional control valves 45, the piston rod of brake cylinder 26 shrinks the brake control lever that makes to brake on dolly and opens, make to brake dolly brake off power.When the spool of control the second electro-hydraulic reversing valve 46 slides into meta, the actuator port B of the second two four-way pilot operated directional control valves 45 is connected with fuel tank, hydraulic oil in brake cylinder 26 rod chambers is back to fuel tank by the second two four-way pilot operated directional control valves 45, brake control lever on braking dolly shrinks the brake shoe and the track that make on brake control lever and produces friction force under the effect of retarding spring, thereby realizes braking.When normal work, need to give the electromagnetic valve energising of the first electro-hydraulic reversing valve 24, the oil inlet of the first electro-hydraulic reversing valve 24 is connected with one of them actuator port B, the hydraulic oil of this actuator port B promotes oil outlet that the first two four-way pilot operated directional control valve 8 commutations make quantitative gear pump 2 and is connected with the oil inlet of the first board-like ball valve 58 through the actuator port of the first two four-way pilot operated directional control valves 8, when needs emergency braking, the electromagnetic valve power-off of the first electro-hydraulic reversing valve 24, the actuator port B of the first electro-hydraulic reversing valve 24 loses oil pressure, the first two four-way pilot operated directional control valves 8 reset its actuator port B are communicated with fuel tank, hydraulic oil in brake cylinder 26 rod chambers is back to fuel tank by the first two four-way pilot operated directional control valves 8, brake control lever on braking dolly shrinks the brake shoe and the track that make on brake control lever and produces friction force under the effect of retarding spring, thereby realize emergency braking.
Shown in Fig. 4, Clamping Circuit comprises the second check valve 60, the 3rd check valve 61, pressure sensor 27, little hydraulic accumulator 28, the first by pass valve 43, clamping oil cylinder 29 and two cover pressure tester 62, two actuator ports of two way variable displacement pump 1 are connected with several clamping oil cylinders 29 by the second check valve 60 and the 3rd check valve 61 respectively, in loop, be connected with the oil inlet place that pressure sensor 27, little hydraulic accumulator 28 and the first by pass valve 43, two cover pressure tester 62 are connected on respectively clamping oil cylinder 29.
Clamping Circuit principle of work: Clamping Circuit pressure adopts two way variable displacement pump 1 delivery pressure, when load increases, two way variable displacement pump 1 delivery pressure increases, Clamping Circuit pressure improves simultaneously, clamping oil cylinder 29 can provide larger gripping power, friction force on assurance walking dolly between drive wheel and track, little hydraulic accumulator 28 can play the effect of repairing and steady pressure in clamping process.
Shown in Fig. 5, start loop and comprise hydraulic hand-pump 11, large hydraulic accumulator 12, pressure stop valve 13, the second by pass valve 42, the first two-position four-way hand valve 17, the board-like ball valve 20 of primer fluid pressure motor 18, second, the 4th check valve 63 and the 5th check valve 64.The oil outlet of hydraulic hand-pump 11 is connected with the oil inlet P of the first two-position four-way hand valve 17 by the second board-like ball valve 20, one of them actuator port of the first two-position four-way hand valve 17 is connected with the oil inlet of primer fluid pressure motor 18, large hydraulic accumulator 12 and the second by pass valve 42 are connected between hydraulic hand-pump 11 and the second board-like ball valve 20, the oil outlet of quantitative gear pump 2 is entering by the 4th check valve 63 and the 5th check valve 64 and the second board-like ball valve 20 respectively, oil outlet is connected, the oil inlet of pressure stop valve 13 is connected with the oil outlet of quantitative gear pump 2.
Start loop works process: when needs start diesel motor, open the second board-like ball valve 20 and the first two-position four-way hand valve 17, pressure oil in large hydraulic accumulator 12 is entered in primer fluid pressure motor 18, primer fluid pressure motor 18 is rotated, if the oil pressure in large hydraulic accumulator 12 is inadequate, can increase pressure in 11 to its by hydraulic hand-pump, in course of normal operation, oriental toothed gear pump 2 also can be by the 4th check valve 63 to large hydraulic accumulator 12 pressure stores oil.Pressure stop valve 13 be after the high pressure oil of brake cylinder 26 returns to fuel tank completely when off-load lotus state, can guarantee gear type pump 2 Low-pressure load discharges, reduce the heating of loss in efficiency and system.
Shown in Fig. 6, Throttle Opening Control loop comprises two tubular ball valves 21, two Remote control valves 22, the second shuttle valve 48 and hydraulic throttle actuators 49.The oil outlet of quantitative gear pump 2 is connected with the oil inlet of two Remote control valves 22 by two tubular ball valves 21 respectively, and the oil outlet of two Remote control valves 22 is connected with hydraulic throttle actuator 49 by the second shuttle valve 48.Two Remote control valves 22 respectively with former and later two operator'ies compartment of monorail crane locomotive in, chaufeur can controlled and entered the hydraulic fluid pressure in hydraulic throttle actuator 49 by Remote control valve 22 in operator's compartment arbitrarily, thereby realizes the control to diesel motor throttle.
Shown in Fig. 7, lifting beam work loop comprises low pressure ball valve 34, the second two-position four-way hand valve 9, the 6th check valve 65, the 3rd by pass valve 66, the 7th check valve 67 and four quick couplings 51.The oil outlet of quantitative gear pump 2 is connected with the oil inlet P of the second two-position four-way hand valve 9 by the 6th check valve 65, one of them actuator port of the second two-position four-way hand valve 9 is connected with two quick couplings 51 wherein by the 7th check valve 67, two other quick coupling 51 is connected with fuel tank 52, and the 3rd by pass valve 66 is connected between the 6th check valve 65 and the second two-position four-way hand valve 9.On fuel tank 52, be connected with level sensor 35, air filter 36, liquid level liquid thermometer 39 and temperature sensor 40, between fuel tank and system, be connected with radiator 37.
Lifting beam work loop works process: when needs carry out crane lifting service, control the second two-position four-way hand valve 9 commutations and cut off the fuel feeding of 2 pairs of brakings of quantitative gear pump and direction control circuit, three position four-way directional control valve 57 two ends control ports lose pressure, the swash plate that stroking mechanism 54 is controlled two way variable displacement pump 1 is got back to meta, the actuator port of two way variable displacement pump 1 does not have delivery pressure, walking loop and Clamping Circuit quit work, and the second two-position four-way hand valve 9 has also cut off the fuel feeding that starts loop and Throttle Opening Control loop simultaneously.The high pressure oil of quantitative gear pump 2 outputs arrives two quick coupling in parallel 51 places successively after the 6th check valve 65, the second two-position four-way hand valve 9 and the 7th check valve 67, quick coupling 51 is connected with the HM Hydraulic Motor of lifting beam, thereby controls the HM Hydraulic Motor work of lifting beam.
Shown in Fig. 8, boost-up circuit comprises pressure charging valve 32 and stacked compression release valve 31, the oil inlet of stacked compression release valve 31 is connected with the oil outlet of the first board-like ball valve 58, the oil outlet of stacked compression release valve 31 is connected with the oil inlet of pressure charging valve 32, and the oil outlet of pressure charging valve 32 is connected with the oil inlet of clamping oil cylinder 29.Inadequate or track is moist skid in the situation that at Clamping Circuit gripping power, utilize the pressure in braking and direction control circuit to provide gripping power in the backward Clamping Circuit of boost-up circuit supercharging, thereby prevent that drive wheel from skidding.
Above-described embodiment is described preferred implementation of the present utility model; not scope of the present utility model is limited; do not departing under the prerequisite of the utility model design spirit; various distortion and improvement that those of ordinary skills make the technical solution of the utility model, all should fall in the definite protection domain of the utility model claims.
Claims (5)
1. a monorail crane locomotive hydraulic control device, comprises walking loop, Clamping Circuit, braking and direction control circuit, startup loop, Throttle Opening Control loop and lifting beam work loop, is wherein characterised in that:
Described walking loop comprises diesel motor (3), two way variable displacement pump (1), slippage pump (53), stroking mechanism (54), DA control cock (56), pressure shut-off valve (68) and several HM Hydraulic Motor (6), described diesel motor (3) is for driving two way variable displacement pump (1) and slippage pump (53) to produce high pressure oil, the actuator port of the HM Hydraulic Motor (6) that two actuator ports of described two way variable displacement pump (1) are in parallel with several is connected, the swash plate of two way variable displacement pump (1) is controlled by stroking mechanism (54), two actuator ports of described stroking mechanism (54) are connected respectively at two actuator ports of three position four-way directional control valve (57), the oil inlet P of described three position four-way directional control valve (57) is connected with the oil outlet of slippage pump (53) by DA control cock (56), the oil inlet of described pressure shut-off valve (68) is connected with the oil inlet P of three position four-way directional control valve (57), the startup control port of pressure shut-off valve (68) is connected with two actuator ports of two way variable displacement pump (1) by shuttle valve, the oil outlet of described slippage pump (53) is connected with the oil inlet of low pressure relief valve (67),
Braking and direction control circuit comprise quantitative gear pump (2), the first board-like ball valve (58), the first shuttle valve (59), the first two four-way pilot operated directional control valves (8), the second two four-way pilot operated directional control valves (45), brake cylinder (26), the first electro-hydraulic reversing valve (24) and the second electro-hydraulic reversing valve (46), described quantitative gear pump (2) drives by diesel motor (3), the oil outlet of quantitative gear pump (2) simultaneously with the first two four-way pilot operated directional control valves (8), the second two four-way pilot operated directional control valves (45), the oil inlet P of the first electro-hydraulic reversing valve (24) and the second electro-hydraulic reversing valve (46) is connected, two actuator ports of described the first electro-hydraulic reversing valve (24) are connected with two hydraulic control hydraulic fluid ports of the first two four-way pilot operated directional control valves (8) respectively, two actuator ports of described the second electro-hydraulic reversing valve (46) are connected with two hydraulic control hydraulic fluid ports of three position four-way directional control valve (57), by the first shuttle valve (59), be connected with the left side hydraulic control hydraulic fluid port of the second two four-way pilot operated directional control valves (45) simultaneously, one of them actuator port of one of them actuator port of described the first two four-way pilot operated directional control valves (8) and the second two four-way pilot operated directional control valves (45) is connected with the import of the first board-like ball valve (58), the outlet of described the first board-like ball valve (58) is connected with the rod chamber of some brake cylinders (26), in the rodless cavity of described brake cylinder (26), pressure spring is installed,
Clamping Circuit comprises the second check valve (60), the 3rd check valve (61), pressure sensor (27), little hydraulic accumulator (28), the first by pass valve (43), clamping oil cylinder (29) and two cover pressure tester (62), two actuator ports of two way variable displacement pump (1) are connected with several clamping oil cylinders (29) by the second check valve (60) and the 3rd check valve (61) respectively, in loop, be connected with pressure sensor (27), little hydraulic accumulator (28) and the first by pass valve (43), two cover pressure tester (62) are connected on respectively the oil inlet place of clamping oil cylinder (29),
Start loop and comprise hydraulic hand-pump (11), large hydraulic accumulator (12), pressure stop valve (13), the second by pass valve (42), the first two-position four-way hand valve (17), primer fluid pressure motor (18), the second board-like ball valve (20), the 4th check valve (63) and the 5th check valve (64), the oil outlet of hydraulic hand-pump (11) is connected with the oil inlet P of the first two-position four-way hand valve (17) by the second board-like ball valve (20), one of them actuator port of described the first two-position four-way hand valve (17) is connected with the oil inlet of primer fluid pressure motor (18), described large hydraulic accumulator (12) and the second by pass valve (42) are connected between hydraulic hand-pump (11) and the second board-like ball valve (20), the oil outlet of described quantitative gear pump (2) is entering by the 4th check valve (63) and the 5th check valve (64) and second board-like ball valve (20) respectively, oil outlet is connected, the oil inlet of described pressure stop valve (13) is connected with the oil outlet of quantitative gear pump (2),
Throttle Opening Control loop comprises two tubular ball valves (21), two Remote control valves (22), the second shuttle valve (48) and hydraulic throttle actuator (49), the oil outlet of described quantitative gear pump (2) is connected with the oil inlet of two Remote control valves (22) by two tubular ball valves (21) respectively, and the oil outlet of two described Remote control valves (22) is connected with hydraulic throttle actuator (49) by the second shuttle valve (48);
Lifting beam work loop comprises low pressure ball valve (34), the second two-position four-way hand valve (9), the 6th check valve (65), the 3rd by pass valve (66), the 7th check valve (67) and four quick couplings (51), the oil outlet of quantitative gear pump (2) is connected with the oil inlet P of the second two-position four-way hand valve (9) by the 6th check valve (65), one of them actuator port of described the second two-position four-way hand valve (9) is connected with two quick couplings (51) wherein by the 7th check valve (67), two other quick coupling (51) is connected with fuel tank (52), described the 3rd by pass valve (66) is connected between the 6th check valve (65) and the second two-position four-way hand valve (9).
2. monorail crane locomotive hydraulic control device according to claim 1, it is characterized in that: described walking loop also comprises high-pressure overflow valve (55) and flushing and Fill valve (69), the oil inlet of two described high-pressure overflow valves (68) is connected with the actuator port of two way variable displacement pump (1) respectively, described flushing is connected with the actuator port of two way variable displacement pump (1) respectively with two actuator ports of Fill valve (69), rinses and is connected with fuel tank with the return opening of Fill valve (69).
3. monorail crane locomotive hydraulic control device according to claim 1, it is characterized in that: described walking loop also comprises two six-way transfer valves (7), the described HM Hydraulic Motor of part (6) is connected on two actuator ports of two way variable displacement pump (1) by two six-way transfer valves (7).
4. monorail crane locomotive hydraulic control device according to claim 1, it is characterized in that: described hydraulic control device also comprises boost-up circuit, described boost-up circuit comprises pressure charging valve (32) and stacked compression release valve (31), the oil inlet of described stacked compression release valve (31) is connected with the oil outlet of the first board-like ball valve (58), the oil outlet of stacked compression release valve (31) is connected with the oil inlet of pressure charging valve (32), and the oil outlet of described pressure charging valve (32) is connected with the oil inlet of clamping oil cylinder (29).
5. monorail crane locomotive hydraulic control device according to claim 1, it is characterized in that: on described fuel tank (52), be connected with level sensor (35), air filter (36), liquid level liquid thermometer (39) and temperature sensor (40), between fuel tank and system, be connected with radiator (37).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320583231.0U CN203486777U (en) | 2013-09-22 | 2013-09-22 | Single-rail crane hydraulic control device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320583231.0U CN203486777U (en) | 2013-09-22 | 2013-09-22 | Single-rail crane hydraulic control device |
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| CN203486777U true CN203486777U (en) | 2014-03-19 |
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| CN201320583231.0U Withdrawn - After Issue CN203486777U (en) | 2013-09-22 | 2013-09-22 | Single-rail crane hydraulic control device |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103508321A (en) * | 2013-09-22 | 2014-01-15 | 北京凯润机电设备制造有限责任公司 | Hydraulic control device for monorail locomotive |
| CN108488277A (en) * | 2018-05-29 | 2018-09-04 | 凯盛重工有限公司 | A kind of hydraulic system of mining brake shuttle tram |
-
2013
- 2013-09-22 CN CN201320583231.0U patent/CN203486777U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103508321A (en) * | 2013-09-22 | 2014-01-15 | 北京凯润机电设备制造有限责任公司 | Hydraulic control device for monorail locomotive |
| CN103508321B (en) * | 2013-09-22 | 2015-06-24 | 北京凯润机电设备制造有限责任公司 | Hydraulic control device for monorail locomotive |
| CN108488277A (en) * | 2018-05-29 | 2018-09-04 | 凯盛重工有限公司 | A kind of hydraulic system of mining brake shuttle tram |
| CN108488277B (en) * | 2018-05-29 | 2024-03-26 | 凯盛重工有限公司 | Hydraulic system of mining braking shuttle car |
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