CN108394822B - Winch automatic control system - Google Patents
Winch automatic control system Download PDFInfo
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- CN108394822B CN108394822B CN201810148290.2A CN201810148290A CN108394822B CN 108394822 B CN108394822 B CN 108394822B CN 201810148290 A CN201810148290 A CN 201810148290A CN 108394822 B CN108394822 B CN 108394822B
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- 229910000831 Steel Inorganic materials 0.000 claims abstract description 15
- 239000010959 steel Substances 0.000 claims abstract description 15
- 239000007788 liquid Substances 0.000 claims abstract description 7
- 238000001514 detection method Methods 0.000 claims description 19
- 230000000087 stabilizing effect Effects 0.000 claims description 4
- 230000007423 decrease Effects 0.000 claims 1
- 230000008901 benefit Effects 0.000 abstract description 5
- 239000003921 oil Substances 0.000 description 121
- 230000005540 biological transmission Effects 0.000 description 11
- 239000010720 hydraulic oil Substances 0.000 description 9
- 230000006870 function Effects 0.000 description 7
- 230000003111 delayed effect Effects 0.000 description 6
- 238000000034 method Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 238000005056 compaction Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000009347 mechanical transmission Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 239000002689 soil Substances 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/08—Driving gear incorporating fluid motors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/28—Other constructional details
- B66D1/40—Control devices
- B66D1/42—Control devices non-automatic
- B66D1/44—Control devices non-automatic pneumatic of hydraulic
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Manipulator (AREA)
Abstract
The invention discloses a winch automatic control system, which comprises a hydraulic pump communicated with an oil source, a brake control device for controlling the start of winch braking, a mechanical hook starting control device for controlling the start of hook starting, a first control device for controlling hook starting or falling, a pressure source for providing pressure for the first control device, a first valve, an air source for providing low-pressure control, a disc brake for winch braking, a relay valve, a second valve and an automatic control module, wherein the hydraulic pump is connected with the oil source; the relay valve comprises a sixth outlet, a fourth outlet, a fifth outlet and a third control end, wherein the sixth outlet is connected with an air source, the fourth outlet is connected with a disc brake control, and the third control end is connected with an automatic control module; the automatic control module can input an air signal or a liquid signal into the third control end according to the swing amplitude of the hoisting steel wire rope. The invention has the advantages of reliable performance, high efficiency and automatic braking.
Description
Technical Field
The invention relates to a hoisting system, in particular to a hoisting automatic control system.
Background
In the prior art, the dynamic compactor is a machine for compacting the loose soil in the construction engineering, and the working principle is that after the rammer is repeatedly lifted to a certain height, the rammer is put down, and the free-falling rammer compacts the loose soil. At present, three types of transmission devices of the dynamic compactor are adopted, one type is purely mechanical transmission, the other type is purely hydraulic transmission, and the other type is mechanical-hydraulic integrated transmission. Mechanical dynamic compactor: the mechanical finger is mechanical in terms of winding, walking, turning mechanism and the like. Disadvantages: large volume, inconvenient disassembly and assembly, poor safety is forbidden by many work places to get into, advantage: the reliability is good. Hydraulic dynamic compactor: the hydraulic pressure indicates the hoist, walks, and the rotation mechanism is all hydraulic control. Disadvantages: the transmission efficiency is low, the failure rate is high, the maintenance difficulty is high, and the technical skill of maintenance personnel is required to be high. The advantages are that: the volume is small and the weight is light. Mechanical-hydraulic integrated type: the winch of the machine finger is mechanical, the walking of the liquid finger, the rotation and the amplitude variation mechanism are hydraulically controlled. The advantages are that: the winch is mechanically driven, has high efficiency and low failure rate, and other actions (walking and turning) are hydraulic drive, so that the winch is small in size and light in weight. At present, the arrangement of the mechanical-hydraulic integrated transmission device is very unreasonable, the transmission efficiency is low, the hydraulic transmission and the mechanical transmission are mutually interfered, the dynamic compactor is ultra-wide, ultra-long and overweight, the requirements of high-strength dynamic compaction and reliability construction cannot be met, the installation requirements of different operation platforms cannot be met, the arrangement forms of different engines and winches cannot be met, and the installation and modification are very inconvenient. Patent number CN201410168149.0 discloses a machine liquid integral type dynamic compaction machine, and the power transmission route of this scheme is: engine-fluid coupling-transfer case-hydraulic pump and hoist. The defects are that: 1. the engine and the winch are transversely arranged in parallel, the operating platform is ultra-wide, the size is increased, the arrangement of the operating platform equipment is not compact, the operating platform equipment cannot be suitable for the requirements of different operating platforms, and the arrangement can be poor in reliability and stability of the operating platform. 2. The engine is positioned in the middle of the operation platform, and the installation and the maintenance are very inconvenient. 3. The power of the engine is transmitted to the hydraulic pump and needs to pass through the fluid coupling, so that the transmission efficiency is reduced. 4. When the hydraulic pump and the winch work simultaneously, after the power of the engine passes through the hydraulic coupler, one part of the power is transmitted to the hydraulic pump, and the other part of the power is transmitted to the winch. When the dynamic compactor works, the engine power intermittently drives the winch to rotate, when the winch rotates forward, the engine is required to provide power, and when the winch rotates backward, the engine is not required to provide power, and the winch drives the winch to rotate backward by means of free falling of the rammer. The torque transmitted by the engine to the hydraulic pump is high and low, and the torque is unstable, so that the pressure of the hydraulic system of the dynamic compactor greatly fluctuates. Therefore, the hydraulic pump and the winch work interfere with each other, so that the pressure fluctuation of the hydraulic system of the dynamic compactor is large, and the hydraulic system of the dynamic compactor is damaged. Meanwhile, a control system used by the dynamic compactor is basically electrohydraulic mixing, under the complex working environment of the dynamic compactor, the electric control is unreliable and the safety problem is easy to cause, and when the dynamic compactor works, the frequency of reciprocating striking and the energy of hammering directly influence the use of the dynamic compactor, the efficiency and the engineering progress are influenced by the too slow frequency, and the energy is too low, so that more times of hammering are needed, and even the dynamic compactor is ineffective.
Meanwhile, the existing winch braking system is mainly divided into manual braking and braking by controlling the number of rotation turns of the winch. The manual braking can lead operators to be highly stressed, and early braking (braking when working weights such as rammers are not landed) or delayed braking (not timely braking after the working weights such as the rammers are landed) can easily occur; early braking can cause breakage of a steel wire rope or even pulling out a winch from an equipment platform, so that safety accidents are caused; the delayed braking can cause the winch to continue rotating to throw out the steel wire rope, so that the steel wire rope is thrown to the ground and is thrown out from the pulley; in the dynamic compaction operation in the underground tunnel, the operator cannot observe the condition of the rammer falling to the ground, so that the construction cannot be performed. The automatic braking system for controlling the number of the rope throwing through controlling the number of the rotation turns of the winch, because the length of the steel wire rope which is downwards put by each action is set according to a program, the length of the steel wire rope is constant each time, and the sinking depth of each ramming of the rammer is different in actual working conditions due to different ground hardness, the situation of more or less discharge exists, and the braking requirement of the winch under the working conditions cannot be met.
Therefore, the winch automatic control system with reliable performance, high efficiency and automatic braking is necessary.
Disclosure of Invention
The invention aims to solve the technical problems and provide a winch automatic control system which has reliable performance, high efficiency and automatic braking.
The invention is realized by the following technical scheme:
a winch automatic control system comprises a hydraulic pump communicated with an oil source, a brake control device for controlling the start of winch braking, a mechanical hook lifting control device for controlling the start of hook lifting, a first control device for controlling hook lifting or falling, a pressure source for providing pressure for the first control device, a first valve, an air source for providing low-pressure control, a disc brake for winch braking, a relay valve, a second valve and an automatic control module; the first valve comprises a first oil inlet end, a first oil return end, a first oil outlet end, a second oil outlet end, a first control end and a second control end, wherein the first oil inlet end is connected with the hydraulic pump, the first oil return end is connected with the oil return pipeline, the first control end is connected with a first outlet of the first control device, the second control end is connected with a second outlet of the first control device, the first oil outlet end is simultaneously connected with the first buffer valve and the mechanical hook lifting control device, the second oil outlet end is connected with one inlet of the first shuttle valve, and the outlet of the first shuttle valve is connected with the brake control device; the third outlet of the first buffer valve is connected with the other inlet of the first shuttle valve; the relay valve comprises a sixth outlet, a fourth outlet, a fifth outlet and a third control end, wherein the sixth outlet is connected with an air source, the fourth outlet is connected with a disc brake control, and the third control end is connected with an automatic control module; the automatic control module can input an air signal or a liquid signal into the third control end according to the swing amplitude of the hoisting steel wire rope; the second valve comprises a fourth control end, a fifth control end, a second oil inlet end, a second oil return end and a third oil outlet end; the fifth outlet is controlled and connected with the fourth control end, the fifth control end is connected with the outlet of the second shuttle valve, two inlets of the second shuttle valve are respectively connected with the first outlet and the second outlet, the second oil inlet end is connected with the hydraulic pump, the second oil return end is connected with an external oil return pipeline, the third oil outlet end and the second oil outlet end are respectively connected with two inlets of the third shuttle valve, and the outlet of the third shuttle valve is connected with the inlet of the first shuttle valve.
Preferably, the automatic control module comprises a first control valve, a second control valve, a third control valve, a fourth control valve and a detection unit for detecting the swing amplitude of the hoisting steel wire rope; one end of the first control valve is connected with a control port of the third control valve, and the other end of the first control valve is connected with an air source through a fourth control valve; one end of the third control valve is connected with an air source, the other end of the third control valve is connected with one end of the second control valve, and the other end of the second control valve is connected with the third control end; the detection unit is in control connection with the first control valve and the second control valve.
Preferably, the detection unit is a cylinder or an oil cylinder, and comprises a signal detection end, an air inlet and an air outlet, wherein the air inlet is connected with an air source, and the air outlet is in control connection with a first control valve and a second control valve.
Preferably, the signal detection end is a piston or a piston rod in the cylinder, and the front end of the signal detection end is provided with a roller.
Preferably, the air source is connected with the detection unit, the fourth control valve and the third control valve through manual switches respectively.
Preferably, the hydraulic control system further comprises a third valve, a seventh outlet of the third valve is connected with a fifth outlet, an eighth outlet of the third valve is connected with a fourth control end, and a sixth control end of the third valve is connected with a pressure source.
Preferably, the hydraulic lifting hook control device, the fourth valve, the second control device for controlling the hydraulic lifting hook or the hydraulic lifting hook to fall, the fifth shuttle valve, the sixth shuttle valve, the second buffer valve, the third buffer valve and the seventh shuttle valve are further included; the third oil inlet end of the second control device is connected with a pressure source, the ninth outlet of the second control device is simultaneously connected with an external forward rotation control oil way and one inlet of a fifth shuttle valve, and the tenth outlet of the second control device is simultaneously connected with an external reverse rotation control oil way and the other inlet of the fifth shuttle valve; the fourth valve comprises a seventh control end, an eighth control end, a fourth oil outlet end, a fourth oil inlet end and a third oil return end; the third oil return end is connected with an external oil return pipeline; the fourth oil inlet end is connected with a hydraulic pump; the fourth oil outlet end is simultaneously connected with the hydraulic hook lifting control device and the third buffer valve, the outlet of the third buffer valve is connected with one inlet of the seventh shuttle valve, the other inlet of the seventh shuttle valve is connected with the outlet of the first shuttle valve, and the outlet of the seventh shuttle valve is connected with the brake control device; the outlet of the fifth shuttle valve is simultaneously connected with the seventh control end and one inlet of the sixth shuttle valve, the outlet of the second shuttle valve is connected with the second buffer valve, the eleventh outlet of the second buffer valve is simultaneously connected with the eighth control end and the other inlet of the sixth shuttle valve, and the outlet of the sixth shuttle valve is connected with the fifth control end.
Preferably, the pressure source connection is connected to the remaining lines via a first manual valve.
Preferably, the mechanical hook lifting control device further comprises a torque converter, and the mechanical hook lifting control device is in control connection with the torque converter.
Preferably, the hydraulic pump is connected with an accumulator with pressure stabilizing function.
The beneficial effects are that: compared with the prior art, the winch automatic control system is connected into the brake control device and the mechanical hook lifting control device through the pressure source and the first valve, the first control device controls different flow directions of the oil way, the sequential starting of the mechanical hook lifting control device and the brake control device is completed under the action of the first buffer valve, stable hook lifting is realized, or the brake control device is independently started, quick landing is realized, corresponding operation is completed through pure mechanical hydraulic drive, the winch system does not need to adopt electric control, and the equipment is stable in operation and high in reliability; meanwhile, as the pipelines are all the mixture of oil and gas pipelines, mechanical hook lifting power is sufficient, and the releasing of the brake is equivalent to the free release when the hooks are put, the speed is high, so that the overall efficiency is high; the winch automatic control system provided by the invention detects through the automatic control module, controls the disc brake to brake in time through the relay valve, and has a quick response and a good braking effect.
Drawings
The invention is described in further detail below with reference to the attached drawing figures, wherein:
FIG. 1 is a basic piping diagram of a hoist autonomous system;
FIG. 2 is a piping control diagram of a winch automatic control system according to the present invention;
FIG. 3 is a circuit control diagram embodiment of a self-control module;
FIG. 4 is a simplified diagram of the hoisting operation of FIG. 3;
fig. 5 is a piping control diagram of a winch automatic control system according to an embodiment of the present invention.
Detailed Description
As shown in fig. 1, a winch automatic control system includes a hydraulic pump 10 connected to an oil source (not shown), a brake control device 20 for controlling the start of winch braking, a mechanical hook start control device 30 for controlling the start of hook start, a first control device 60 for controlling hook start or drop, a pressure source 70 for providing pressure to the first control device 60, and a first valve 110, wherein the first valve 110 includes a first oil inlet end 111, a first oil return end 112, a first oil outlet end 113, a second oil outlet end 114, a first control end 115, and a second control end 116, the first oil inlet end 111 is connected to the hydraulic pump 10, the first oil return end 112 is connected to an external oil return line for pressure relief, the first control end 115 is connected to a first outlet 601 of the first control device 60, the second control end 116 is connected to a second outlet 602 of the first control device 60, the first oil outlet end 113 is simultaneously connected to the first buffer valve 31 and the mechanical hook start control device 30, the second oil outlet end 114 is connected to an inlet of one of the first shuttle valves 201, and the outlet of the first shuttle valves 201 is connected to the brake control device 20; the third outlet 311 of the first trim valve 31 is connected to the other inlet of the first shuttle valve 201.
The first control device 60 is a valve or a push rod controlled manually, or may be a two-position two-way valve, and the hydraulic fluid of the pressure source 70 enters the first control device 60, so that the operator controls the oil path to flow out from the first outlet 601 or the second outlet 602 by setting the opening state of the first control device 60.
As described in the above paragraph, when the oil from the first outlet 601 enters the first control end 115, the device is in a hooked state, the first oil inlet 111 is communicated with the first oil outlet 113, the second oil outlet 114 is communicated with the first oil return 112, and the hydraulic oil from the first shuttle valve 201 to the second oil outlet 114 returns to the external oil return pipeline along the first oil return 112; meanwhile, the hydraulic pump 10, the first oil inlet end 111, the first oil outlet end 113 and the mechanical hook lifting control device 30 are in pipeline communication, the mechanical hook lifting control device 30 is jacked in and connected with a winch power motor (not shown in the drawing), at the moment, the brake control device 20 is still in a working state, a brake (not shown in the drawing) in transmission connection with the hydraulic pump is still used for braking the winch, hydraulic oil reaching the first oil outlet end 113 slowly passes through the first buffer valve 31, so that the hydraulic oil slowly enters the first shuttle valve 201 in a delayed manner, then enters the brake control device 20 from the first shuttle valve 201, at the moment, the brake control device 20 is jacked up, the brake is released, the equipment can normally lift the hook, and the aim of delayed starting is to prevent dangerous situations that weights fall to the ground due to the fact that the power does not reach the brake at the moment of lifting the hook. When the oil from the second outlet 602 enters the second control end 116, the device is in a hook-falling state, the first oil inlet end 111 is communicated with the second oil outlet end 114, the first oil outlet end 113 is communicated with the first oil return end 112, and the hydraulic oil from the mechanical hook-lifting control device 30 to the first oil outlet end 113 returns to an external oil return pipeline along the first oil return end 112; meanwhile, the hydraulic pump 10, the first oil inlet end 111, the second oil outlet end 114 and the brake control device 20 are communicated through pipelines, the brake control device 20 is jacked up, the brake is loosened, the hook is normally released under the condition of no load, the falling speed is high, and the phase change efficiency is improved.
In the preferred embodiment, as shown in fig. 2, the winch automatic control system can also be added with an air source 40 for providing low pressure control, a disc brake 50 for winch braking, a relay valve 51, a second valve 120 and an automatic control module 410; the relay valve 51 comprises a sixth outlet 511, a fourth outlet 512, a fifth outlet 513 and a third control end 514, the sixth outlet 511 is connected with the air source 40, the fourth outlet 512 is in control connection with the disc brake 50, the third control end (514) is connected with the outlet of the eighth shuttle valve 400, and the self-control module 410 and an external pipeline can be respectively connected with two inlets of the eighth shuttle valve 400; so that the effect of the disc brake 50 can be flexibly controlled regardless of whether the external pipe is controlled by the self-control module 410 or manually. The external pipeline can be a foot brake or a hand brake and the like. The self-control module 410 can input an air signal or a liquid signal into the third control end 514 according to the swing amplitude of the hoisting steel wire rope so as to control the disc brake 50 to automatically brake, prevent the steel wire rope from loosening due to untimely braking after landing, and prevent the steel wire rope from being broken due to falling to the ground when the braking is controlled manually.
The second valve 120 includes a fourth control end 121, a fifth control end 122, a second oil inlet end 123, a second oil return end 124, and a third oil outlet end 125; the fifth outlet 513 is in control connection with the fourth control end 121, the fifth control end 122 is connected with the outlet of the second shuttle valve 610, two inlets of the second shuttle valve 610 are respectively connected with the first outlet 601 and the second outlet 602, the second oil inlet end 123 is connected with the hydraulic pump 10, the second oil return end 124 is connected with an external oil return pipeline, the third oil outlet end 125 and the second oil outlet end 114 are respectively connected with two inlets of the third shuttle valve 202, and an outlet of the third shuttle valve 202 is connected with an inlet of the first shuttle valve 201.
The hooking and unhooking oil path processes are identical with respect to the pipe states described in the first to third paragraphs, except that the control of the high pressure passage by the external low pressure control pipe is achieved by the air source 40. The low pressure pipeline can be filled with gas, or low pressure hydraulic oil can be selected, and the principle of low pressure control of high pressure is the same. The gas is described here as an example: intake air is provided from the third control end 514, and the sixth outlet 511 communicates with both the fourth outlet 512 and the fifth outlet 513. The air source 40, the relay valve 51 and the disc brake 50 are communicated through pipelines, and the disc brake 50 enables a braking function, so that flexible control is facilitated for personnel; meanwhile, the air source 40, the relay valve 51, the second valve 120 are communicated through a pipeline, the fourth control end 121 is used for air intake, the second oil inlet end 123 is communicated with the third oil outlet end 125, the oil source 10, the second valve 120, the third shuttle valve 202, the first shuttle valve 201 and the brake control device 20 are communicated through a pipeline, the brake control device 20 is jacked up, and the brake is released. When the third control end 514 is not in air, control oil flows out from the outlet of the second shuttle valve 610 to the fifth control end 122, the third oil outlet 125 communicates with the second oil return 124, and hydraulic oil in the pipeline is drained from the oil return pipeline. The external incoming air can be controlled by foot brake or manual operation, and can be automatically input by the automatic control module 410, so that the diversity and the flexible activation of the functions of the winch automatic control system are realized.
The self-control module 410 can be controlled by adopting electric elements, such as electromagnetic contact, an inductor and the like, and the change of components on the winch, such as the straightening condition of a steel wire rope, the swinging amplitude or the rotation number of the winch equipment, is sensed, but the control detection means are easy to lose effectiveness under the complex working condition of the dynamic compactor, and the embodiment of the pure hydraulic control of the self-control module 410 provided herein has the advantages of reliable work, complex working condition resistance and quick response.
As shown in fig. 3, the self-control module 410 includes a first control valve 414, a second control valve 415, a third control valve 416, a fourth control valve 413, and a detection unit 412 for detecting the swing amplitude of the hoisting wire rope;
one end of the first control valve 414 is connected with a control port of the third control valve 416, and the other end of the first control valve 414 is connected with the air source 40 through the fourth control valve 413; one end of the third control valve 416 is connected with the air source 40, the other end of the third control valve 416 is connected with one end of the second control valve 415, the other end of the second control valve 415 is connected with the third control end 514, and the outlet of the second shuttle valve 610 is connected with the fourth control valve 413 in a control manner;
the detecting unit 412 may be a force sensitive or photosensitive sensor, but is preferably a cylinder or an oil cylinder, the detecting unit 412 includes a signal detecting end 412c, an air inlet 412a and an air outlet 412b, the signal detecting end 412c is in contact with the hoisting wire rope, the air inlet 412a is connected to the air source 40, and the air outlet 412b is in control connection with the first control valve 414 and the second control valve 415.
In the automatic braking stage, the signal detection end 412c detects a corresponding signal, and the air inlet 412a is communicated with the air outlet 412 b: the control port of the first control valve 414 is used for air intake, and the control port of the fourth control valve 413 communicated to the third control valve 416 is used for preparing for the subsequent brake release; the control port of the second control valve 415 is used for air intake, the second control valve 415 is communicated with elements connected with two ends, and the air source 40, the third control valve 416, the second control valve 415 and the control port of the relay valve 51 are communicated through the whole pipeline; the third control end 514 of the relay valve 51 is used for feeding air, the relay valve 51 is communicated with the elements connected with the two ends, and the whole pipeline of the air source 40, the relay valve 51 and the first control end of the disc brake 50 is communicated; the disc brake 50 is hydraulically driven to effect an action brake.
In the brake release stage, air or oil is introduced from the outlet of the second shuttle valve 610 to the control port of the fourth control valve 413, and if the fourth control valve 413 itself has a cutoff function, the control line may be omitted for simplification. The fourth control valve 413 is communicated with the elements connected with the two ends, and the control port pipelines of the air source 40, the fourth control valve 413, the first control valve 414 and the third control valve 416 are communicated; the control port of the third control valve 416 is filled with air, and the third control valve 416 disconnects the elements connected to the two ends; the third control end 514 of the relay valve 51 stops the air supply, the valve connection is reset, and the relay valve 51 disconnects the elements connected at the two ends; the disc brake 50 releases the hydraulic drive.
In a preferred embodiment, as shown in fig. 3, the signal detecting end 412c is a piston or a piston rod in a cylinder, and a roller 412d is disposed at the front end of the signal detecting end 412c to prevent the signal detecting end 412c from wearing in the process of directly pressing against the wire rope.
In the preferred embodiment, as shown in fig. 3, the air source 40 is connected to the detecting unit 412, the fourth control valve 413 and the third control valve 416 through the manual switch 411, respectively, so as to cut off the pipeline when necessary.
As shown in fig. 4, the winch is a simple device to which the winch automatic control system described above is applied. The device comprises a winch drum 1, a disc brake 50, a steel wire rope 11 extending from the winch drum 1, a detection unit 412 and a relay valve 51 connected with the disc brake 50; the detecting unit 412 includes a signal detecting end 412c and a signal output end 42, where the signal detecting end 412c is in contact with the wire rope 11 to determine the swing amplitude of the wire rope 11, and since the wire rope 11 is in a straightened state during the process of hanging and releasing a heavy object, the wire rope 11 can apply a pulling force or a pressing force to the signal detecting end 412c, and after the signal detecting end 412c detects a change of the force, it can determine that the swing amplitude of the wire rope changes, and then moves, so that the air inlet 412a is communicated with the air outlet 412b, and then is transmitted to the relay valve 51 through a combination of a plurality of control valves, such as a combination of the first control valve 414, the third control valve 416 and the second control valve 415 shown in fig. 4, and the relay valve 51 controls the disc brake 50 to perform braking according to the gas-liquid signal. It should be clear that in fig. 2 and 3, the self-control module 410 is connected to the air source 40, but not shown in fig. 4, the self-control module 410 may be connected to another air source 40 independently from the viewpoint of design, even if the self-control module 410 itself includes an independent air supply device, and the connection of the two devices may simplify the piping, particularly, the design is preferred.
In the preferred embodiment, as shown in fig. 2 and 3, the valve further comprises a third valve 130, the seventh outlet 131 of the third valve 130 is connected to the fifth outlet 513, the eighth outlet 132 of the third valve 130 is connected to the fourth control end 121, and the sixth control end 133 of the third valve 130 is connected to the pressure source 70. The first manual valve 71 is connected to the pressure source 70, and the control oil of the pressure source 70 always enters the third valve 130 to ensure that the eighth outlet 132 is communicated with the seventh outlet 131, and the oil path is directly disconnected through the first manual valve 71 when needed, so that the eighth outlet 132 and the seventh outlet 131 are disconnected, and the safety disconnection of the whole control pipeline is realized.
In a preferred embodiment, as shown in fig. 2, the air source 40 is connected to one of the inlets of the fourth shuttle valve 41 through the second manual valve 42, the eighth outlet 132 is connected to the other inlet of the fourth shuttle valve 41, and the outlet of the fourth shuttle valve 41 is connected to the fourth control end 121, so that the air source 40 provides a flow of control air to the fourth control end 121 when the rest is not supplied with oil or gas, and the safety disconnection of the entire control line is achieved by disconnecting the second manual valve 42 when necessary.
When the dynamic compactor works, the frequency of reciprocating striking and the energy of hammering directly influence the use of the dynamic compactor, the efficiency and the engineering progress are influenced by too slow frequency, so that more hammering is needed due to too low energy, the efficiency is low, even the dynamic compaction is not effective, the mechanical control energy is usually larger but can not be controlled slightly, and the condition that the hook is slightly lifted or put on for adjustment can not be met.
Embodiments of integrated control of the machine and fluid are provided herein, including a hydraulic lift hook control device 80 for micro-control operation and co-generation of force, a fourth valve 140, a second control device 90 for controlling hydraulic lift hook or drop, a fifth shuttle valve 100, a sixth shuttle valve 150, a second buffer valve 160, a third buffer valve 170, and a seventh shuttle valve 180.
As shown in fig. 5, the third oil inlet 91 of the second control device 90 is connected to the pressure source 70, the ninth outlet 92 of the second control device 90 is simultaneously connected to the external normal rotation control oil path and one inlet of the fifth shuttle valve 100, and the tenth outlet 93 of the second control device 90 is simultaneously connected to the external reverse rotation control oil path and the other inlet of the fifth shuttle valve 100.
As shown in fig. 5, the fourth valve 140 includes a seventh control end 141, an eighth control end 142, a fourth oil outlet end 143, a fourth oil inlet end 144, and a third oil return end 145; the third oil return end 145 is connected with an external oil return pipeline; the fourth oil inlet end 144 is connected with the hydraulic pump 10; the fourth oil outlet 143 is simultaneously connected to the hydraulic hook control device 80 and the third buffer valve 170, an outlet of the third buffer valve 170 is connected to one inlet of the seventh shuttle valve 180, another inlet of the seventh shuttle valve 180 is connected to an outlet of the first shuttle valve 201, and an outlet of the seventh shuttle valve 180 is connected to the brake control device 20.
As shown in fig. 5, the outlet of the fifth shuttle valve 100 is simultaneously connected to the seventh control terminal 141 and one inlet of the sixth shuttle valve 150, the outlet of the second shuttle valve 610 is connected to the second buffer valve 160, the eleventh outlet 161 of the second buffer valve 160 is simultaneously connected to the eighth control terminal 142 and the other inlet of the sixth shuttle valve 150, and the outlet of the sixth shuttle valve 150 is connected to the fifth control terminal 122.
The hooking process, the low pressure control pipe control high pressure passage process from the outside air supply, and the automatic braking process of the present embodiment are identical with respect to the pipe states described in the first to seventeenth paragraphs. The newly added part is specifically described here: the second control device 90 is a valve or a push rod controlled manually, or may be a two-position two-way valve, and the hydraulic fluid of the pressure source 70 enters the second control device 90, and the operator controls the oil path to flow out from the ninth outlet 92 or the tenth outlet 93 by setting the opening state of the first control device 60. The difference between the oil output from the ninth outlet 92 and the tenth outlet 93 is that the forward and reverse rotation start of an external oil path (not shown) is controlled, the oil path may be grafted with a multiway valve (not shown), or two oil path embodiments may be separately provided depending on the design of the external oil path, and the subsequent control of the hydraulic hook lifting control device 80 after the oil output from the ninth outlet 92 and the tenth outlet 93 is consistent, which is not separately described.
The second control device 90 is started, control oil sequentially passes through the fifth shuttle valve 100 and the sixth shuttle valve 150 and enters the fifth control end 122, and the third oil outlet end 125 is communicated with the second oil return end 124 to realize pressure relief; meanwhile, control oil enters the seventh control end 141 through the fifth shuttle valve 100, the fourth oil outlet end 143 is communicated with the fourth oil inlet end 144, the oil source 10, the fourth valve 140 and the hydraulic hook lifting control device 80 are communicated through a pipeline, the hydraulic hook lifting control device 80 is started and connected with hydraulic drive (not shown in the figure), at the moment, the brake control device 20 is still in a working state, a brake (not shown in the figure) in transmission connection with the brake control device is still used for braking a winch, hydraulic oil to the fourth oil outlet end 143 slowly passes through the third buffer valve 170, so that the hydraulic oil is delayed to enter the seventh shuttle valve 180, then enters the brake control device 20 from the seventh shuttle valve 180, at the moment, the brake control device 20 is propped up, the brake is released, the equipment can lift the hook normally, and the aim of delayed start is to prevent the dangerous situation that a heavy object falls down due to the fact that the power does not reach the brake at the moment of lifting the hook.
As shown in fig. 5, in the oil path of the mechanical part, the second buffer valve 160 is disposed at the outlet of the second shuttle valve 610, and the purpose is that when the pressure source 70 supplies oil to both the second control device 90 and the first control device 60, the control oil entering from the second control device 90 first goes into the seventh control port 141 so that the fourth oil outlet port 143 communicates with the fourth oil inlet port 144, and the control oil entering from the first control device 60 enters the eighth control port 142 slowly due to the second buffer valve 160, the former passage is already opened, and the left and right pressures are equal, so that the passage cannot be cut off. When the second control device 90 is in the neutral position and stops running, the fourth valve 140 returns under the condition that the eighth control end 142 is in oil feeding, the fourth oil outlet end 143 is communicated with the third oil return end 145, and the hydraulic oil between the fourth valve 140 and the hydraulic hook lifting control device 80 is discharged along the oil return pipeline, so that the corresponding function is finally completed.
The preferred embodiment, as shown in fig. 1, 2, 3 and 5, further comprises a torque converter 34, the mechanical hook lifting control device 30 is in control connection with the torque converter 34, and can be directly connected with the brake control device 20 for control starting, and also can be arranged through an oil way, so that when the mechanical hook lifting control device 30 is started, the torque converter is also started together, the winch is started and power is transmitted through the torque converter, and the effective torque conversion buffering is realized, so that the equipment is stable in operation and sufficient in power.
In the preferred embodiment, as shown in fig. 1, 2, 3 and 5, the pressure source 70 is connected to the rest of the pipelines through the first manual valve 71, so that each control pipeline can be conveniently and emergently closed when needed, and the safety is ensured.
In the preferred embodiment, as shown in fig. 1, 2, 3 and 5, the hydraulic pump 10 is connected to an external oil return line through a relief valve 102 to prevent excessive pressure overflow. The relief valve 102 may be one of a pressure relief valve, a ball valve, a one-way sequence valve, or a time delay valve.
In the preferred embodiment, as shown in fig. 1, 2, 3 and 5, the hydraulic pump 10 is connected with an accumulator 101 with pressure stabilizing function, so as to prevent the pressure in the system from being too low and always stabilizing at a normal value.
In the preferred embodiment, the first buffer valve 31, the second buffer valve 160, and the third buffer valve 170 are one of a one-way sequence valve and a delay valve, so long as the function of one-way delay is achieved.
In the preferred embodiment, the brake control device 20, the mechanical hook lifting control device 30 and the hydraulic hook lifting control device 80 are cylinders, and of course, may be common execution elements of hydraulic systems, such as hydraulic motors: gear type hydraulic motors, vane hydraulic motors, plunger hydraulic motors, and the like. The clutch control device can only play a role in controlling the clutch of the winch automatic control system and the power device.
The above embodiments are only for illustrating the technical solution of the present invention and not for limiting the same, and any modifications or equivalent substitutions without departing from the spirit and scope of the present invention should be covered in the scope of the technical solution of the present invention.
Claims (7)
1. The utility model provides a hoist automatic control system, includes hydraulic pump (10) of intercommunication oil supply, control hoist and hold brake and launch brake controlling means (20), control the mechanical hook lifting controlling means (30) that hook lifting launched, control hook lifting or first controlling means (60) that decline and give pressure source (70) of pressure, its characterized in that is provided for first controlling means (60):
the winch brake further comprises a first valve (110), an air source (40) for providing low-pressure control, a disc brake (50) for winch braking, a relay valve (51), a second valve (120) and an automatic control module (410);
the first valve (110) comprises a first oil inlet end (111), a first oil return end (112), a first oil outlet end (113), a second oil outlet end (114), a first control end (115) and a second control end (116), wherein the first oil inlet end (111) is connected with the hydraulic pump (10), the first oil return end (112) is connected with an oil return pipeline, the first control end (115) is connected with a first outlet (601) of the first control device (60), the second control end (116) is connected with a second outlet (602) of the first control device (60), the first oil outlet end (113) is connected with the first buffer valve (31) and the mechanical hook lifting control device (30), the second oil outlet end (114) is connected with one inlet of the first shuttle valve (201), and an outlet of the first shuttle valve (201) is connected with the brake control device (20);
a third outlet (311) of the first buffer valve (31) is connected to the other inlet of the first shuttle valve (201);
the relay valve (51) comprises a sixth outlet (511), a fourth outlet (512), a fifth outlet (513) and a third control end (514), wherein the sixth outlet (511) is connected with the air source (40), the fourth outlet (512) is in control connection with the disc brake (50), and the third control end (514) is connected with the automatic control module (410);
the automatic control module (410) can input a gas signal or a liquid signal into the third control end (514) according to the swing amplitude of the hoisting steel wire rope;
the second valve (120) comprises a fourth control end (121), a fifth control end (122), a second oil inlet end (123), a second oil return end (124) and a third oil outlet end (125); the fifth outlet (513) is in control connection with the fourth control end (121), the fifth control end (122) is connected with an outlet of a second shuttle valve (610), two inlets of the second shuttle valve (610) are respectively connected with the first outlet (601) and the second outlet (602), the second oil inlet end (123) is connected with the hydraulic pump (10), the second oil return end (124) is connected with an external oil return pipeline, the third oil outlet end (125) and the second oil outlet end (114) are respectively connected with two inlets of a third shuttle valve (202), and an outlet of the third shuttle valve (202) is connected with an inlet of the first shuttle valve (201);
the automatic control module (410) comprises a first control valve (414), a second control valve (415), a third control valve (416), a fourth control valve (413) and a detection unit (412) for detecting the swing amplitude of the hoisting steel wire rope;
one end of the first control valve (414) is connected with a control port of the third control valve (416), and the other end of the first control valve (414) is connected with the air source (40) through the fourth control valve (413);
one end of the third control valve (416) is connected with the air source (40), the other end of the third control valve (416) is connected with one end of the second control valve (415), and the other end of the second control valve (415) is connected with the third control end (514);
the detection unit (412) is in control connection with the first control valve (414) and the second control valve (415);
the detection unit (412) is a cylinder or an oil cylinder, the detection unit (412) comprises a signal detection end (412 c), an air inlet (412 a) and an air outlet (412 b), the air inlet (412 a) is connected with the air source (40), and the air outlet (412 b) is in control connection with the first control valve (414) and the second control valve (415);
the signal detection end (412 c) is a piston or a piston rod in the cylinder, and a roller (412 d) is arranged at the front end of the signal detection end (412 c).
2. The hoist robot of claim 1, characterized in that: the air source (40) is respectively connected with the detection unit (412), the fourth control valve (413) and the third control valve (416) through a manual switch (411).
3. The hoist robot of claim 1, characterized in that: the hydraulic control system further comprises a third valve (130), wherein a seventh outlet (131) of the third valve (130) is connected with the fifth outlet (513), an eighth outlet (132) of the third valve (130) is connected with the fourth control end (121), and a sixth control end (133) of the third valve (130) is connected with the pressure source (70).
4. The hoist robot of claim 1, characterized in that: the hydraulic lifting hook control device (80), a fourth valve (140), a second control device (90) for controlling the hydraulic lifting hook or falling, a fifth shuttle valve (100), a sixth shuttle valve (150), a second buffer valve (160), a third buffer valve (170) and a seventh shuttle valve (180) are further included;
the third oil inlet end (91) of the second control device (90) is connected with the pressure source (70), the ninth outlet (92) of the second control device (90) is connected with an external forward rotation control oil way and one inlet of the fifth shuttle valve (100), and the tenth outlet (93) of the second control device (90) is connected with an external reverse rotation control oil way and the other inlet of the fifth shuttle valve (100);
the fourth valve (140) comprises a seventh control end (141), an eighth control end (142), a fourth oil outlet end (143), a fourth oil inlet end (144) and a third oil return end (145); the third oil return end (145) is connected with an external oil return pipeline; the fourth oil inlet end (144) is connected with the hydraulic pump (10); the fourth oil outlet end (143) is connected with the hydraulic hook lifting control device (80) and the third buffer valve (170), the outlet of the third buffer valve (170) is connected with one inlet of the seventh shuttle valve (180), the other inlet of the seventh shuttle valve (180) is connected with the outlet of the first shuttle valve (201), and the outlet of the seventh shuttle valve (180) is connected with the brake control device (20);
the outlet of the fifth shuttle valve (100) is connected with the seventh control end (141) and one inlet of the sixth shuttle valve (150), the outlet of the second shuttle valve (610) is connected with the second buffer valve (160), the eleventh outlet (161) of the second buffer valve (160) is connected with the eighth control end (142) and the other inlet of the sixth shuttle valve (150), and the outlet of the sixth shuttle valve (150) is connected with the fifth control end (122).
5. The hoist robot of claim 1, characterized in that: the pressure source (70) is connected to the remaining lines via a first manual valve (71).
6. The hoist robot of claim 1, characterized in that: further comprises a torque converter (34), and the mechanical hook lifting control device (30) is in control connection with the torque converter (34).
7. The hoist robot of claim 1, characterized in that: the hydraulic pump (10) is connected with an accumulator (101) with a pressure stabilizing function.
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| CN201810148290.2A CN108394822B (en) | 2018-02-13 | 2018-02-13 | Winch automatic control system |
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| JPH11335085A (en) * | 1998-05-26 | 1999-12-07 | Hitachi Constr Mach Co Ltd | Safety device for construction machine |
| CN202063662U (en) * | 2011-03-29 | 2011-12-07 | 瑞安市昌盛建筑工程机械厂 | Winding engine |
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