CN101229907B - Coil diameter sensitive constant-speed constant-tension hydraulic winch and controlling method thereof - Google Patents
Coil diameter sensitive constant-speed constant-tension hydraulic winch and controlling method thereof Download PDFInfo
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- CN101229907B CN101229907B CN2007103052455A CN200710305245A CN101229907B CN 101229907 B CN101229907 B CN 101229907B CN 2007103052455 A CN2007103052455 A CN 2007103052455A CN 200710305245 A CN200710305245 A CN 200710305245A CN 101229907 B CN101229907 B CN 101229907B
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Abstract
The invention discloses a coil diameter sensitive hydraulic winch with constant speed and constant tension and a controlling method thereof. The winch comprises a variable displacement motor and a coil diameter sensitive control system. When working, output torque of the variable displacement motor increases with the increase of the coil diameter by using the coil diameter sensitive control system. Thus, the structure can use output power of hydraulic source with high efficiency for promoting the working performance of the winch; when the actual output tension of the hydraulic source is higher than rating tension, the winch can provide higher speed or tension than a designed value; when the actual load tension is lower than the rating tension, the winch can provide the highest speed under the condition of safe operation with the load.
Description
Technical field
The present invention relates to capstan winch, relate in particular to coil diameter sensitive constant-speed constant-tension hydraulic winch.
Background technology
Along with popularizing of capstan winch, its purposes constantly enlarges, and not only uses as the instrument of saving oneself on outdoor activity car, cross-country car, truck, also is used widely in industry.When the needs pulling force is little, can adopt electric capstan, but big and require the occasion of continuous working for pulling force, just can't be competent at by electric capstan, at this moment just need hydraulic windlass.Hydraulic windlass of the prior art is generally specified pulling force capstan winch, and torque is constant in the output procedure.Speed did not increase when its shortcoming was to draw weight, and motor is wasted discharge capacity when drawing light thing.And the pulling force of its each layer and the linear velocity of steel rope all change with the variation of the coil diameter of wire rope roll on the reel, and this requires constant occasion to some pulling force and linear velocity, and a steady speed can't be provided on demand exactly, equably.For this reason, the constant-speed constant-tension capstan winch that uses fixed displacement motor and double drum type or storage rope roll formula physical construction to combine is also arranged, but the capstan winch overall volume of this physical construction is big, price is very high abroad, such price can't be born by domestic consumer.Therefore never applied.
Summary of the invention
The purpose of this invention is to provide coil diameter sensitive constant-speed constant-tension hydraulic winch and control method thereof, hydraulic power source specified delivery pressure is provided and keep constant and situation that load force is also constant under, the speed that makes capstan winch be operated in each layer keeps constant.Can save under the condition of cost, utilize the horsepower output of hydraulic power source efficiently, improve the serviceability of capstan winch as much as possible, when hydraulic power source real output pressure ratio rated pressure was higher, capstan winch is higher speed or bigger pulling force in the time of can providing than standard duty; When the actual loading pulling force was lower than specified pulling force, capstan winch can provide than faster speed under the rated load, nominal load situation.No matter be in which kind of mode of operation, capstan winch can both keep the feature of constant-speed constant-tension as long as can work.
In order to reach described purpose, described coil diameter sensitive constant-speed constant-tension hydraulic winch adopts the change displacement motor in the course of the work, and the output torque that utilizes the coil diameter sensitive control system to make to become displacement motor increases with the increase of coil diameter.
Preferably, the coil diameter sensitive system comprises the solenoid directional control valve that connects fuel tank, and solenoid directional control valve has A, the output of B two-way, and A routing electromagnet change-over valve is connected in the hydraulic control variable-dis-placement motor through one-way throttle valve one; B routing electromagnet change-over valve is connected to balance cock through one-way throttle valve two, balance cock is connected in the hydraulic control variable-dis-placement motor, also be connected with on the one-way throttle valve two and connecting the fixedly pressure reduction control ratio flow regulating valve of damper, the pressure reduction control ratio flow regulating valve other end also is connected in the hydraulic control variable-dis-placement motor, the other end also is connected in the hydraulic control variable-dis-placement motor, and the balance cock on the B road is connected the A road near hydraulic control variable-dis-placement motor place.Such structure relies on the closed condition of balance cock to realize the braking of capstan winch.
Preferably, described coil diameter sensitive system comprises the solenoid directional control valve that connects fuel tank, and solenoid directional control valve has A, the output of B two-way, and A routing electromagnet change-over valve is connected in the hydraulic control variable-dis-placement motor through one-way throttle valve one; B routing electromagnet change-over valve is connected to hydraulic control one-way valve through one-way throttle valve two, hydraulic control one-way valve is connected in the hydraulic control variable-dis-placement motor, also be connected with on the one-way throttle valve two and connecting the fixedly pressure reduction control ratio flow regulating valve of damper, the pressure reduction control ratio flow regulating valve other end also is connected in the hydraulic control variable-dis-placement motor, and the hydraulic control one-way valve on the B road is connected with the one-way throttle valve junction with A road solenoid directional control valve.Such structure relies on the closed condition of hydraulic control one-way valve and mechanical braking to realize double brake.
Preferably, described coil diameter sensitive system comprises the solenoid directional control valve that connects fuel tank, solenoid directional control valve has A, the output of B two-way, in the A road direct connection hydraulic control variable-dis-placement motor, the B road is connected in the hydraulic control variable-dis-placement motor by balance cock, fuel tank is connected into the solenoid directional control valve place and is provided with manual throttle valve, and the described balance cock of manual throttle valve is connected in the pressure reduction control throttle by solenoid directional control valve.
Preferably, described coil diameter sensitive system comprises the solenoid directional control valve that connects fuel tank, and solenoid directional control valve has A, the output of B two-way, and A routing electromagnet change-over valve is connected in the hydraulic control variable-dis-placement motor through one-way throttle valve one; B routing electromagnet change-over valve is connected to balance cock through one-way throttle valve two, balance cock is connected in the hydraulic control variable-dis-placement motor, also be connected with on the hydraulic control variable-dis-placement motor control mouth and connecting the fixedly pressure reduction control ratio flow regulating valve of damper, all the other two ends of pressure reduction control ratio flow regulating valve are connected to the two ends of one-way throttle valve two, and the balance cock on the B road is connected the A road near hydraulic control variable-dis-placement motor place.The speed that such structure is transferred by the balance cock control load.
Preferably, described coil diameter sensitive system all is arranged on the oil circuit board.Maintenance the time can disassemble replacing with the monoblock oil circuit board like this, and is convenient and swift, also guaranteed the stability of total system.
Owing to adopted described structure, the present invention adopts hydraulic control variable-dis-placement motor and coil diameter sensitive system can automatically keep the pulling force of each layer of capstan winch and linear velocity constant, make the primary mover of oil supply system always work in best efficiency point, improve the system capacity degree of utilization, have remarkable energy saving effect.
Description of drawings
The invention will be further described below in conjunction with accompanying drawing:
Fig. 1 concerns scheme drawing for coil diameter sensitive constant-speed constant-tension hydraulic winch hydraulic control variable-dis-placement motor control presssure of the present invention and discharge capacity.
Fig. 2 is coil diameter sensitive constant-speed constant-tension hydraulic winch embodiment 1 scheme drawing of the present invention.
Fig. 3 is coil diameter sensitive constant-speed constant-tension hydraulic winch embodiment 2 scheme drawings of the present invention.
Fig. 4 is coil diameter sensitive constant-speed constant-tension hydraulic winch embodiment 3 scheme drawings of the present invention.
Fig. 5 is coil diameter sensitive constant-speed constant-tension hydraulic winch embodiment 4 (1) scheme drawings of the present invention.
Fig. 6 is coil diameter sensitive constant-speed constant-tension hydraulic winch embodiment 4 (2) scheme drawings of the present invention.
The specific embodiment
The control method of coil diameter sensitive constant-speed constant-tension hydraulic winch of the present invention is: adopt to become displacement motor in the course of the work, utilize by the coil diameter sensitive control system output torque that becomes displacement motor is increased with the increase of coil diameter.
In entire work process, the output torque of motor increases with coil diameter, becomes displacement motor by adopting, and utilizes the coil diameter sensitive control system, change displacement motor output torque is increased with the increase of coil diameter, thereby keep capstan winch to keep constant in the pulling force and the linear velocity of each layer.
Because bearing power satisfies following relational expression:
P
Load=FV
Therefore, under the situation of load pulling force and constant airspeed, its power P
LoadConstant.From the conservation energy angle, the power of load and motor satisfies following relational expression:
P
Load=P
Motorη
η is a mechanical efficiency in the formula.Suppose that mechanical efficiency is a constant.Then require motor can adapt to the variation of load, be always load constant horsepower output is provided.
The motor horsepower output satisfies following relational expression:
P
Motor=Δ p * q
Δ p is the motor inlet outlet pressure differential in the formula, and q is the flow of motor of flowing through.
Therefore, keep constant, just can make the motor horsepower output keep constant as long as guarantee the flow of motor and inlet outlet pressure differential.
The vertical hoisting heavy of needs according to whether proposes two kinds of fluid control solutions:
One: at the vertical hoisting heavy of needs or to the stationarity of transferring process the situation of specific (special) requirements is arranged, adopt balance cock 2, cancel the mechanical braking unit simultaneously as brak control unit.Balance cock 2 is in braking and transfer in the process and work, and the influence of balancing gravity makes the process of transferring steadily controlled.
Two:, adopt hydraulic control one-way valve 4 as brake unit at the situation that does not need vertical hoisting heavy.The pressure of its control mouth 1 and the relation of discharge capacity are as shown in Figure 1.
Be illustrated in figure 2 as the embodiment of the invention 1:
When drawing load wherein:
Working connection: under this operating mode, solenoid directional control valve 9 works in right position.High pressure oil is got back to fuel tank through solenoid directional control valve 9, one-way throttle valve 26, balance cock 2, hydraulic control variable-dis-placement motor, one-way throttle valve 1, solenoid directional control valve 9.
Guide's oil circuit:
Pressure reduction control ratio flow regulating valve 7 constitutes a hydraulic pressure half-bridge with fixing damper 8, control mouth 1 pressure of control hydraulic control variable-dis-placement motor.The inlet pressure of one-way throttle valve 26 acts on the spool right side control chamber area of pressure reduction control ratio flow regulating valve 7, and simultaneously, the delivery pressure p2 of one-way throttle valve 26 acts on the spool left side control chamber area of pressure reduction control ratio flow regulating valve (7).The spool that the inlet outlet pressure differential Δ p=p1-p2 of one-way throttle valve 26 makes pressure reduction control ratio flow regulating valve 7 is to left movement, and retracing spring is installed in the spool of pressure reduction control ratio flow regulating valve 7 left side, and this initial tension of spring moves right spool.Under the state of equilibrium, initial tension of spring and the formed equivalent thrust equal and opposite in direction of the inlet outlet pressure differential of one-way throttle valve 26, direction are opposite.
Control principle: the inlet outlet pressure differential of the discharge capacity increase → hydraulic control variable-dis-placement motor B road pressure minimizing → one-way throttle valve 26 delivery pressure minimizing → one-way throttle valves 26 of the control mouth 1 pressure minimizing → hydraulic control variable-dis-placement motor of the valve port flow area minimizing → hydraulic control variable-dis-placement motor of the inlet outlet pressure differential minimizing → pressure reduction control ratio flow regulating valve 7 of capstan winch coil diameter increase → load torque increase → hydraulic control variable-dis-placement motor B road pressure increase → one-way throttle valve 26 delivery pressure increasing → one-way throttle valves 26 increases.
By the variation tendency of related variable in the oil circuit in the above-mentioned control process as can be seen, this control system constitutes a negative feedback loop.By the appropriate design pressure reduction control ratio flow regulating valve 7 and the fixing parameter of damper 8, can keep the inlet outlet pressure differential of one-way throttle valve 1 to keep constant.Because the flow Q of one-way throttle valve 1 and the relation of its inlet outlet pressure differential Δ P meet following mathematical relation:
C in the formula
dBeing coefficient of flow, is constant, generally gets 0.64; For the valve port opening of manual one-way throttle valve 1, can set up by hand, be constant for the particular job process; ρ is a fluid density, generally gets 870 kilograms per cubic meter.
Therefore, the flow through flow Q of one-way throttle valve 1 keeps constant.If the pressure P that oil sources provides
SKeep constant, it is constant that the pressure reduction of two working oil path of hydraulic control variable-dis-placement motor also can keep.The power of hydraulic control variable-dis-placement motor output also keeps constant as can be known.Therefore, under load pressure unmodified situation, it is constant that load speed also keeps, and the variation with coil diameter does not change.
In sum, under the operating mode of tractive load, oil circuit shown in Figure 2 can be realized the controlled target to the constant-speed constant-tension of load.
When transferring load:
Working connection:
Solenoid directional control valve 9 works in position, a left side.High pressure oil is got back to fuel tank through solenoid directional control valve 9, one-way throttle valve 1, hydraulic control variable-dis-placement motor, balance cock 2, one-way throttle valve 26, solenoid directional control valve 9.
Guide's oil circuit:
Guide's control oil channel of hydraulic control variable-dis-placement motor with on identical when drawing load.At this moment, inlet outlet pressure differential Δ p=p1-p2＜0 of one-way throttle valve 1, pretend hydraulic coupling on the spool that is used for pressure reduction control ratio flow regulating valve 7 and spring force direction all to the right, then pressure reduction control ratio flow regulating valve 7 is in closed condition all the time, guide's control presssure P of hydraulic control variable-dis-placement motor
x=0, the discharge capacity of hydraulic control variable-dis-placement motor remains on maximum rating.Guide's control presssure of balance cock 2 comes the A road of hydraulic pressure independent variable motor, under this operating mode, balance cock 2 works, this valve plays self-equalizing gravity, make hydraulic control variable-dis-placement motor A road pressure remain on setting value, the stall under the effect of gravity load of hydraulic control variable-dis-placement motor, the speed of transferring by balance cock 2 and one-way throttle valve 1 control load together.
Braking
Working connection:
Solenoid directional control valve 9 works in meta.Its actuator port all links to each other with return opening, is in depressurization phase.
Guide's oil circuit:
At this moment, the inlet outlet pressure differential Δ p=p1-p2=0 of one-way throttle valve 26, pretend the spool that is used for pressure reduction control ratio flow regulating valve 7 and be in closed condition all the time under the effect of spring force, guide's control presssure of hydraulic control variable-dis-placement motor is zero, and the discharge capacity of hydraulic control variable-dis-placement motor remains on maximum rating.Guide's control presssure of balance cock 2 is from the A road of hydraulic control variable-dis-placement motor, and under this operating mode, this control presssure is zero, and balance cock 2 is closed, and the hydraulic control variable-dis-placement motor is in braking mode.
Be illustrated in figure 3 as embodiment of the invention 2:: described coil diameter sensitive system comprises the solenoid directional control valve 9 that connects fuel tank, and solenoid directional control valve 9 has A, the output of B two-way, and A routing electromagnet change-over valve 9 is connected in the hydraulic control variable-dis-placement motor through one-way throttle valve 1; B routing electromagnet change-over valve 9 is connected to hydraulic control one-way valve 4 through one-way throttle valve 26, hydraulic control one-way valve 4 is connected in the hydraulic control variable-dis-placement motor, also be connected with on the one-way throttle valve 26 and connecting the fixedly pressure reduction control ratio flow regulating valve 7 of damper 8, pressure reduction control ratio flow regulating valve 7 other ends also are connected in the hydraulic control variable-dis-placement motor control mouth 1, and the hydraulic control one-way valve 4 on the B road is connected with one-way throttle valve one 3 junctions with A road solenoid directional control valve 9.
When on being in, drawing load, working connection:
Solenoid directional control valve 9 works in right position.High pressure oil is got back to fuel tank through solenoid directional control valve 9, one-way throttle valve 26, hydraulic control one-way valve 4, hydraulic control variable-dis-placement motor, one-way throttle valve 1, solenoid directional control valve 9.
Guide's oil circuit:
Pressure reduction control ratio flow regulating valve 7 constitutes a hydraulic pressure half-bridge with fixing damper 8, control mouth 1 pressure of control hydraulic control variable-dis-placement motor.The inlet pressure of one-way throttle valve 26 acts on the spool right side control chamber area of pressure reduction control ratio flow regulating valve 7, and simultaneously, the delivery pressure p2 of one-way throttle valve 26 acts on the spool left side control chamber area of pressure reduction control ratio flow regulating valve (7).The spool that the inlet outlet pressure differential Δ p=p1-p2 of one-way throttle valve 26 makes pressure reduction control ratio flow regulating valve 7 is to left movement, and retracing spring is installed in the spool of pressure reduction control ratio flow regulating valve 7 left side, and this initial tension of spring moves right spool.Under the state of equilibrium, initial tension of spring and the formed equivalent thrust equal and opposite in direction of the inlet outlet pressure differential of one-way throttle valve 26, direction are opposite.
Guide's control presssure of hydraulic control one-way valve 4 is from the A road of solenoid directional control valve 9, and under this operating mode, pressure oil enters the B road of hydraulic control variable-dis-placement motor by the positive dirction of one-way throttle valve 26, and is irrelevant with its guide's control-oil pressure.
Transfer load
Working connection:
Solenoid directional control valve 9 works in position, a left side.
High pressure oil through solenoid directional control valve 9, one-way throttle valve 1,, hydraulic control one-way valve 4, one-way throttle valve 26, solenoid directional control valve 9 get back to fuel tank.
Guide's oil circuit:
At this moment, the inlet outlet pressure differential Δ p=p1-p2=0 of one-way throttle valve 26, pretend hydraulic coupling on the spool that is used for pressure reduction control ratio flow regulating valve 7 and spring force direction all to the right, then pressure reduction control ratio flow regulating valve 7 is in closed condition all the time, guide's control presssure of hydraulic control variable-dis-placement motor is zero, and the discharge capacity of hydraulic control variable-dis-placement motor remains on maximum rating.
Guide's control presssure of hydraulic control one-way valve 4 is from the A road of solenoid directional control valve 9, and under this operating mode, solenoid directional control valve A road pressure leads to high pressure, forces to make hydraulic control one-way valve 4 be in opening, guarantees the working connection conducting.Like this can be by mechanical brake and one-way throttle valve 1 lowering velocity of control load together.
Braking
Working connection:
Solenoid directional control valve 9 works in meta.Its actuator port all links to each other with return opening, is in depressurization phase.
Guide's oil circuit:
At this moment, the inlet outlet pressure differential of one-way throttle valve 1, pretend the spool that is used for pressure reduction control ratio flow regulating valve 7 and be in closed condition all the time under the effect of spring force, the guide of hydraulic control variable-dis-placement motor controls and presses is zero, and the discharge capacity of hydraulic control variable-dis-placement motor remains on maximum rating.
Guide's control presssure of hydraulic control one-way valve 4 is from the A road of solenoid directional control valve 9 at this moment, and under this operating mode, this control presssure is zero, and hydraulic control one-way valve 4 is closed, and the hydraulic control variable-dis-placement motor is in braking mode.
Be illustrated in figure 4 as the embodiment of the invention 3: described coil diameter sensitive system comprises the solenoid directional control valve 9 that connects fuel tank, solenoid directional control valve 9 has A, the output of B two-way, in the A road direct connection hydraulic control variable-dis-placement motor, the B road is connected in the hydraulic control variable-dis-placement motor by balance cock 2, fuel tank is connected into the solenoid directional control valve place and is provided with manual throttle valve 11, and manual throttle valve 11 is connected in the pressure reduction control throttle 7 by solenoid directional control valve 9 with described balance cock 2
On draw load
Working connection:
Under this operating mode, solenoid directional control valve 9 works in right position.
High pressure oil is got back to fuel tank through one-way throttle valve 11, solenoid directional control valve 9, balance change-over valve 3, hydraulic control variable-dis-placement motor, solenoid directional control valve 9.
Guide's oil circuit:
Pressure reduction control throttle 5 constitutes a hydraulic pressure half-bridge with fixed restrictor 7, control mouth 1 pressure of control hydraulic control variable-dis-placement motor.The inlet pressure of manual throttle valve 11 acts on the spool right side control chamber area of pressure reduction control throttle 5, and simultaneously, the delivery pressure of manual throttle valve 11 acts on the spool left side control chamber area of pressure reduction control throttle 5.The inlet outlet pressure differential of manual throttle valve 11 makes the spool of pressure reduction control throttle 5 to left movement, and retracing spring is installed in the spool of pressure reduction control throttle 5 left side, and this initial tension of spring moves right spool.Under the state of equilibrium, initial tension of spring and the formed equivalent thrust equal and opposite in direction of the inlet outlet pressure differential of manual throttle valve 11, direction are opposite.
Control principle: the inlet outlet pressure differential of discharge capacity Vg rising → hydraulic control variable-dis-placement motor B road pressure decay → manual throttle valve 11 delivery pressure decline → manual throttle valves 11 of the control port pressure P X decline → hydraulic control variable-dis-placement motor of the valve port flow area decline → hydraulic control variable-dis-placement motor of the inlet outlet pressure differential decline → pressure reduction control throttle 5 of capstan winch coil diameter rising → load torque rising → hydraulic control variable-dis-placement motor B road pressure rising → manual throttle valve 11 delivery pressure rising → manual throttle valves 11 rises
When being in when transferring load working connection:
Solenoid directional control valve 9 works in position, a left side.High pressure oil is through manually flow regulating valve 11, solenoid directional control valve 9, hydraulic control variable-dis-placement motor, balance cock 2, solenoid directional control valve 9 are got back to fuel tank.
Guide's oil circuit:
Guide's control oil channel of hydraulic control variable-dis-placement motor with on identical when drawing load.
Guide's control presssure of balance cock 2 is from the A mouth of hydraulic control variable-dis-placement motor, under this operating mode, balance cock works, the effect of this valve self-equalizing gravity, make hydraulic control variable-dis-placement motor A mouth pressure remain on setting value, avoid the stall under the effect of gravity load of hydraulic control variable-dis-placement motor.
The speed that transferred by balance cock 2 and manual throttle valve 11 control load together this moment.
The glancing impact working connection:
Solenoid directional control valve 9 works in meta.Its actuator port all links to each other with return opening, is in depressurization phase.
Guide's oil circuit:
Guide's control oil channel of hydraulic control variable-dis-placement motor with on described identical when drawing load.At this moment, the inlet outlet pressure differential of manual throttle valve 11 is pretended the spool that is used for pressure reduction control throttle 5 and be in closed condition all the time under the effect of spring force, and guide's control presssure of hydraulic control variable-dis-placement motor is zero, and the discharge capacity of hydraulic control variable-dis-placement motor remains on maximum rating.
Guide's control presssure of balance cock 2 is from the A road of hydraulic control variable-dis-placement motor, and under this operating mode, this control presssure is zero, and balance cock 2 is closed, and the hydraulic control variable-dis-placement motor is in braking mode.The main braking that relies on the closed condition realization capstan winch of balance cock.
Freely turn round
Working connection:
Solenoid directional control valve 9 works in meta.Its actuator port all links to each other with return opening, is in depressurization phase.
Guide's oil circuit:
Guide's control oil channel of hydraulic control variable-dis-placement motor with on described identical when drawing load.At this moment, the inlet outlet pressure differential of manual throttle valve 11 is pretended the spool that is used for pressure reduction control throttle 5 and be in closed condition all the time under the effect of spring force, and guide's control presssure of hydraulic control variable-dis-placement motor is zero, and the discharge capacity of hydraulic control variable-dis-placement motor remains on maximum rating.
Guide's control presssure of balance cock 2 is from the input pressure hydraulic fluid port, and under this operating mode, this control presssure is a high pressure, and balance cock 2 is forced to open, and the hydraulic control variable-dis-placement motor is in free turn state.
By the open mode that guide's high pressure forces balance cock to be in, realize the free revolute function of capstan winch.
Shown in Fig. 5,6, be the embodiment of the invention 4.Because the access way of pressure reduction control ratio flow regulating valve 7 is different, embodiment 4 specifically has two kinds of mounting meanss.
On draw load
Embodiment 4 (1) as shown in Figure 5:
Pressure reduction control ratio flow regulating valve 7 constitutes a Type B hydraulic pressure half-bridge, the pressure of the control mouth 1 of control variable motor with fixing damping 8.The inlet pressure of one-way throttle valve 26 acts on the spool downside control chamber area of pressure reduction control ratio flow regulating valve 7, and simultaneously, the delivery pressure of one-way throttle valve 26 acts on the spool upside control chamber area of pressure reduction control ratio flow regulating valve 7.The spool upside of pressure reduction control ratio flow regulating valve 7 is equipped with retracing spring, and this spring has the predetermincd tension that spool is moved downward.On this, draw under the load behavior, the inlet outlet pressure differential of one-way throttle valve 26＞0 acts on the spool two ends, generation makes the thrust of the spool upward movement of pressure reduction control ratio flow regulating valve 7, when the spool of pressure reduction control ratio flow regulating valve 7 reaches state of equilibrium, manually the formed equivalent thrust of inlet outlet pressure differential of one-way throttle valve 26 and initial tension of spring equal and opposite in direction, direction are opposite, thereby the valve port flow area of controlling pressure reduction control ratio flow regulating valve 7 is to control its delivery pressure.
Under the another kind of connection mode, embodiment 4 (2) as shown in Figure 6:
Two valve ports in the pressure reduction control ratio flow regulating valve 7 constitute an A type hydraulic pressure half-bridge together, draw the guide from its 3rd valve port and control fluid, with the pressure of 1 mouthful in the control mouth of control variable motor.The inlet pressure of one-way throttle valve 26 acts on the spool right side control chamber area of pressure reduction control ratio flow regulating valve 7, and simultaneously, the delivery pressure of one-way throttle valve 26 acts on the spool left side control chamber area of pressure reduction control ratio flow regulating valve 7.The spool left side of pressure reduction control ratio flow regulating valve 7 is equipped with retracing spring, and this spring has the predetermincd tension that spool is moved right.On this, draw under the load behavior, the inlet outlet pressure differential of one-way throttle valve 26＞0 acts on the spool two ends, generation makes the thrust of the spool of pressure reduction control ratio flow regulating valve 7 to left movement, when the spool of pressure reduction control ratio flow regulating valve 7 reaches state of equilibrium, manually the formed equivalent thrust of inlet outlet pressure differential of one-way throttle valve 26 and initial tension of spring equal and opposite in direction, direction are opposite, thereby the flow area of controlling two valve ports in the pressure reduction control ratio flow regulating valve 7 is to control its delivery pressure.
Control principle:
Embodiment 4 (1) as shown in Figure 5:
The inlet outlet pressure differential of the discharge capacity Vg increase → variable-dis-placement motor B mouth pressure decline → one-way throttle valve 26 delivery pressure decline → one-way throttle valves 26 of the control port pressure P X decline → variable-dis-placement motor of the valve port flow area increase → variable-dis-placement motor of the inlet outlet pressure differential decline → pressure reduction control ratio flow regulating valve 7 of capstan winch coil diameter increase → load torque increase → variable-dis-placement motor B mouth pressure increase → one-way throttle valve 26 delivery pressure increase → one-way throttle valves 26 increases.
Embodiment 4 (2) as shown in Figure 6:
The inlet outlet pressure differential of the discharge capacity Vg increase → variable-dis-placement motor B mouth pressure decline → one-way throttle valve 26 delivery pressure decline → one-way throttle valves 26 of the control port pressure decay → variable-dis-placement motor of first valve port flow area decline → variable-dis-placement motor of the inlet outlet pressure differential decline → pressure reduction control ratio flow regulating valve 7 of capstan winch coil diameter increase → load torque increase → variable-dis-placement motor B mouth pressure increase → one-way throttle valve 26 delivery pressure increase → one-way throttle valves 26 increases
By the variation tendency of related variable in the oil circuit in the above-mentioned control process as can be seen, this control system constitutes a negative feedback loop.By the pressure reduction control ratio flow regulating valve 7 among the appropriate design figure respectively and the fixing parameter of damping 8, can keep the inlet outlet pressure differential Δ P of one-way throttle valve 26 to keep constant.Because the flow Q of one-way throttle valve 26 and the relation of its inlet outlet pressure differential Δ P meet following mathematical relation:
C in the formula
dBeing coefficient of flow, is constant, generally gets 0.75; For the valve port opening of manual one-way throttle valve 26, can set up by hand, be constant for the particular job process; Be fluid density, generally get 870 kilograms per cubic meter.
Therefore, the flow through flow Q of one-way throttle valve 26 keeps constant.If it is constant that the pressure P S that oil sources provides keeps, it is constant that the pressure reduction of two actuator ports of variable-dis-placement motor also can keep.The power of variable-dis-placement motor output that hence one can see that keeps constant last being pulled through in the journey, under load pulling force unmodified situation, pull wire speed also keeps constant on the capstan winch, and the variation with coil diameter does not change.
When transferring load,
Working connection:
Embodiment 4 (1) as shown in Figure 5:
Solenoid directional control valve 9 works in position, a left side.
High pressure oil is got back to fuel tank through solenoid directional control valve 9, one-way throttle valve 1, variable-dis-placement motor, balance cock 2, one-way throttle valve 26, solenoid directional control valve 9.
Embodiment 4 (2) as shown in Figure 6:
Solenoid directional control valve 9 works in position, a left side.
High pressure oil is got back to fuel tank through solenoid directional control valve 9, one-way throttle valve 1, variable-dis-placement motor, balance cock 2, one-way throttle valve 26, solenoid directional control valve 9.
Guide's oil circuit:
Embodiment 4 (1) as shown in Figure 5:
Guide's control oil channel of variable-dis-placement motor with on identical when drawing load, at this moment, the inlet outlet pressure differential Δ p=p1-p2=0 of one-way throttle valve 26, pretend the spool that is used for pressure reduction control ratio flow regulating valve 7 and under the effect of spring force, be in conducting state all the time, guide's control presssure of variable-dis-placement motor is zero, and the discharge capacity of variable-dis-placement motor remains on maximum rating.
Guide's control presssure of balance cock 2 is from the A road of variable-dis-placement motor, and under this operating mode, balance cock 2 works, and the effect of this valve self-equalizing gravity makes variable-dis-placement motor A road pressure remain on setting value, avoids variable-dis-placement motor stall under the effect of gravity load.The i.e. speed of transferring by balance cock 2 control loads.
Embodiment 4 (2) as shown in Figure 6:
Guide's control oil channel of variable-dis-placement motor with on identical when drawing load, at this moment, the inlet outlet pressure differential of one-way throttle valve 26, pretend the spool that is used for pressure reduction control ratio flow regulating valve 7 and under the effect of spring force, be in closed condition all the time, guide's control presssure of variable-dis-placement motor is zero, and the discharge capacity of variable-dis-placement motor remains on maximum rating.
Guide's control presssure of balance cock 2 is from the A road of variable-dis-placement motor, and under this operating mode, balance cock 2 works, and the effect of this valve self-equalizing gravity makes variable-dis-placement motor A road pressure remain on setting value, avoids variable-dis-placement motor stall under the effect of gravity load.The i.e. speed of transferring by balance cock 2 control loads.Glancing impact,
Embodiment 4 (1) as shown in Figure 5:
Working connection:
Solenoid directional control valve 9 works in meta.Its actuator port all links to each other with return opening, is in depressurization phase.Guide's oil circuit:
Guide's control oil channel of variable-dis-placement motor with on described identical when drawing load.At this moment, the inlet outlet pressure differential of one-way throttle valve 26 is pretended the spool that is used for pressure reduction control ratio flow regulating valve 7 and be in conducting state all the time under the effect of spring force, and guide's control presssure of variable-dis-placement motor is zero, and the discharge capacity of variable-dis-placement motor remains on maximum rating.
Guide's control presssure of balance cock 2 is from the A mouth of variable-dis-placement motor, and under this operating mode, this control presssure is zero, and balance cock 2 is closed, and variable-dis-placement motor is in braking mode.
The main braking that relies on the closed condition realization capstan winch of balance cock.
Embodiment 4 (2) as shown in Figure 6:
Solenoid directional control valve 9 works in meta.Its actuator port all links to each other with return opening, is in depressurization phase.Guide's oil circuit:
Guide's control oil channel of variable-dis-placement motor with on described identical when drawing load.At this moment, the inlet outlet pressure differential of one-way throttle valve 26 is pretended the spool that is used for pressure reduction control ratio flow regulating valve 7 and be in closed condition all the time under the effect of spring force, and guide's control presssure of variable-dis-placement motor is zero, and the discharge capacity of variable-dis-placement motor remains on maximum rating.
Guide's control presssure of balance cock 2 is from the A mouth of variable-dis-placement motor, and under this operating mode, this control presssure is zero, and balance cock 2 is closed, and variable-dis-placement motor is in braking mode.
The main braking that relies on the closed condition realization capstan winch of balance cock.
Above-described oil circuit all is incorporated on the oil circuit board, so that install and maintenance.
After adopting the present invention, the performance of whole capstan winch is improved, and is specific as follows:
The working parameter of capstan winch when adopting 28ml/r to become displacement hydraulic motor
| Title | | Unit |
| Pressure | ||
| 12 | MPa | |
| Flow | 38.6 | L/min |
| Transmitting ratio | 147 | NULL |
| The maximum load moment of torsion | 4618 | Nm |
| Maximum motor torsional moment | 39.3 | Nm |
| Specified pulling force | 5448 | Kg |
| Last pulling rate degree | 5 | m/min |
| Net effciency | 0.7 | null |
This shows that 70% efficient is very high, simultaneously can also guarantee stable last a pulling rate degree, this is that the capstan winch of prior art is not being accomplished under the condition of cost on an equal basis.
Be compared as follows with the capstan winch performance of prior art: (to make comparisons) with the situation of 2000 pounds of pulling force
Prior art capstan winch technical parameter:
| Pulling force (pound) | Linear velocity (M/min) | Discharge capacity (ml/r) | Flow (L/min) | Difference of pressure (MPa) | Horsepower input (kw) | The energy utilized rate | |
| Ground floor | 2000 | 11 | 80 | 60 | 2.2 | 2.1 | 60％ |
| The second layer | 2000 | 13.4 | 80 | 60 | 2.7 | 2.6 | 74％ |
| The 3rd layer | 2000 | 15.8 | 80 | 60 | 3.2 | 3.1 | 86％ |
| The 4th layer | 2000 | 18.2 | 80 | 60 | 3.7 | 3.6 | 100％ |
Technical parameter of the present invention
| Pulling force (pound) | Linear velocity (M/min) | Discharge capacity (ml/r) | Flow (L/min) | Difference of pressure (MPa) | Horsepower input (kw) | The energy utilized rate | |
| Ground floor | 2000 | 24 | 8.9 | 60 | 5 | 4.9 | 100％ |
| The second layer | 2000 | 24 | 10.6 | 60 | 5 | 4.9 | 100％ |
| The 3rd layer | 2000 | 24 | 12.7 | 60 | 5 | 4.9 | 100％ |
| The 4th layer | 2000 | 24 | 14.8 | 60 | 5 | 4.9 | 100％ |
This shows:
1. adopt capstan winch of the present invention can automatically regulating under the situation of input flow rate and constant pressure to keep each layer pulling force and linear velocity constant.And the prior art capstan winch can not automatically regulating keeps each layer pulling force and linear velocity constant.
2. under the situation of input flow rate and constant pressure, and under the constant situation of pulling force, the prior art capstan winch at the ground floor propulsion source with 76%, the three layer 88%, the four layer 100% of dose rate 65%. second layer.And among the present invention the propulsion source of each layer with dose rate equal 100%.
3. can improve the linear velocity of capstan winch when underloading with the high speed gear of double speed capstan winch, capstan winch of the present invention linear velocity when system's maximum flow and motor minimum injection rate can reach 24m/min.And prior art capstan winch the 4th layer line speed when system's maximum flow can only reach 18m/min.
To sum up, adopt coil diameter sensitive constant-speed constant-tension hydraulic winch of the present invention and control method thereof as can be known, can automatically keep pulling force of each layer of capstan winch and linear velocity constant, propulsion source dose rate height under the invariable prerequisite of the delivery rate of hydraulic efficiency power unit, under flow system flow unmodified situation, linear velocity then increases when pulling force reduces, and strengthens motor displacement and improve the capstan winch pulling force under ground floor system pressure unmodified situation.The output torque that is particularly useful for motor in the overall process of capstan winch running is changing, and capstan winch is required constant occasion in the pulling force and the linear velocity of each layer.
The present invention works as hydraulic power source real output pulling force when higher than specified pulling force, and capstan winch can provide than higher speed of design value or bigger pulling force; When the actual loading pulling force was lower than specified pulling force, capstan winch can provide under this load state the fastest speed under the safe operation condition.Can automatically regulating under the situation of input flow rate and constant pressure keep each layer pulling force and linear velocity constant, and the propulsion source of each layer be with dose rate 100% under the situation of the big little discharge capacity of flow the capstan winch linear velocity higher by 50% than the capstan winch of prior art.
Claims (6)
1. coil diameter sensitive constant-speed constant-tension hydraulic winch, it is characterized in that: adopt in the course of the work to become displacement motor, the output torque that utilizes the coil diameter sensitive control system to make to become displacement motor increases with the increase of coil diameter, thereby keeps capstan winch to keep constant in the pulling force and the linear velocity of each layer
Because bearing power satisfies following relational expression:
P
Load=FV
Therefore, under the situation of load pulling force and constant airspeed, its power P
LoadConstant, from the conservation energy angle, the power of load and motor satisfies following relational expression:
P
Load=P
Motorη
η is a mechanical efficiency in the formula, and mechanical efficiency is a constant, then requires motor can adapt to the variation of load, be always load constant horsepower output is provided,
The motor horsepower output satisfies following relational expression:
P
Motor=Δ p * q
Δ p is the motor inlet outlet pressure differential in the formula, and q is the flow of motor of flowing through,
Therefore, constant as long as the flow of the motor of guaranteeing to flow through and inlet outlet pressure differential keep, just can make the maintenance of motor horsepower output constant.
2. coil diameter sensitive constant-speed constant-tension hydraulic winch as claimed in claim 1, it is characterized in that: described coil diameter sensitive control system comprises the solenoid directional control valve (9) that connects fuel tank, solenoid directional control valve (9) has A, the output of B two-way, and A routing electromagnet change-over valve (9) is connected to hydraulic control through one-way throttle valve one (3) and becomes in the displacement motor; B routing electromagnet change-over valve (9) is connected to balance cock (2) through one-way throttle valve two (6), balance cock (2) is connected to hydraulic control and becomes in the displacement motor, also be connected with on the one-way throttle valve two (6) and connecting the fixedly pressure reduction control ratio flow regulating valve (7) of damper (8), pressure reduction control ratio flow regulating valve (7) other end also is connected to hydraulic control and becomes in the displacement motor control mouthful (1), and the balance cock on the B road (2) is connected the A road and becomes the displacement motor place near hydraulic control.
3. coil diameter sensitive constant-speed constant-tension hydraulic winch as claimed in claim 1, it is characterized in that: described coil diameter sensitive control system comprises the solenoid directional control valve (9) that connects fuel tank, solenoid directional control valve (9) has A, the output of B two-way, and A routing electromagnet change-over valve (9) is connected to hydraulic control through one-way throttle valve one (3) and becomes in the displacement motor; B routing electromagnet change-over valve (9) is connected to hydraulic control one-way valve (4) through one-way throttle valve two (6), hydraulic control one-way valve (4) is connected to hydraulic control and becomes in the displacement motor, also be connected with on the one-way throttle valve two (6) and connecting the fixedly pressure reduction control ratio flow regulating valve (7) of damper (8), pressure reduction control ratio flow regulating valve (7) other end also is connected to hydraulic control and becomes in the displacement motor control mouthful (1), and the hydraulic control one-way valve on the B road (4) is connected with one-way throttle valve one (3) junction with A road solenoid directional control valve (9).
4. coil diameter sensitive constant-speed constant-tension hydraulic winch as claimed in claim 1, it is characterized in that: described coil diameter sensitive control system comprises the solenoid directional control valve (9) that connects fuel tank, solenoid directional control valve (9) has A, the output of B two-way, the direct connection hydraulic control of A road becomes in the displacement motor, the B road is connected to hydraulic control by balance cock (2) and becomes in the displacement motor, fuel tank is connected into the solenoid directional control valve place and is provided with manual throttle valve (11), and manual throttle valve (11) is connected in the pressure reduction control throttle (5) by solenoid directional control valve (9) with described balance cock (2).
5. coil diameter sensitive constant-speed constant-tension hydraulic winch as claimed in claim 1, it is characterized in that: described coil diameter sensitive control system comprises the solenoid directional control valve (9) that connects fuel tank, solenoid directional control valve (9) has A, the output of B two-way, and A routing electromagnet change-over valve (9) is connected to hydraulic control through one-way throttle valve one (3) and becomes in the displacement motor; B routing electromagnet change-over valve (9) is connected to balance cock (2) through one-way throttle valve two (6), balance cock (2) is connected to hydraulic control and becomes in the displacement motor, also be connected with in the hydraulic control change displacement motor control mouthful (1) and connecting the fixedly pressure reduction control ratio flow regulating valve (7) of damper (8), all the other two ends of pressure reduction control ratio flow regulating valve (7) are connected to the two ends of one-way throttle valve two (6), and the balance cock on the B road (2) is connected the A road and becomes the displacement motor place near hydraulic control.
6. as one of them described coil diameter sensitive constant-speed constant-tension hydraulic winch of claim 2-5, it is characterized in that: described coil diameter sensitive control system all is arranged on the oil circuit board.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007103052455A CN101229907B (en) | 2007-12-26 | 2007-12-26 | Coil diameter sensitive constant-speed constant-tension hydraulic winch and controlling method thereof |
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| CN2007103052455A CN101229907B (en) | 2007-12-26 | 2007-12-26 | Coil diameter sensitive constant-speed constant-tension hydraulic winch and controlling method thereof |
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| CN101229907B true CN101229907B (en) | 2010-11-17 |
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| US9908756B2 (en) | 2012-09-28 | 2018-03-06 | Parker-Hannifin Corporation | Constant pull winch controls |
| CN104564880B (en) * | 2014-12-29 | 2017-03-15 | 中联重科股份有限公司 | Rear axle steering valve group, axle steering centering hydraulic control system and vehicle |
| CN104863564B (en) * | 2015-01-29 | 2019-01-29 | 徐州徐工基础工程机械有限公司 | A kind of horizontal directional drilling machine torque and push-pull effort numerical value display system |
| CN105351284B (en) * | 2015-11-13 | 2017-07-14 | 四川川润液压润滑设备有限公司 | The rotating shaft disintegrating machine and its constant speed control method of a kind of rotating shaft invariablenes turning speed |
| CN106882722B (en) * | 2017-04-14 | 2022-05-03 | 湖南科技大学 | Ocean winch electro-hydraulic braking system based on closed hydraulic brake and control method |
| CN112645163B (en) * | 2020-11-10 | 2022-12-27 | 中国煤炭科工集团太原研究院有限公司 | Cable winding device and control method of cable winding device |
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Address after: 321017, 1689, Yuen Yuan Road, Zhejiang, Jinhua Patentee after: ZHEJIANG NOWVOW MECHANICAL AND ELECTRICAL CORP. Address before: 321016 No. 128, Yuen Lu, Jinhua, Zhejiang Patentee before: Zhejiang Nowvow Mechanical and Electrical Co., Ltd. |