CN201321358Y - Crane hoist control system and crane - Google Patents
Crane hoist control system and crane Download PDFInfo
- Publication number
- CN201321358Y CN201321358Y CNU2008201791664U CN200820179166U CN201321358Y CN 201321358 Y CN201321358 Y CN 201321358Y CN U2008201791664 U CNU2008201791664 U CN U2008201791664U CN 200820179166 U CN200820179166 U CN 200820179166U CN 201321358 Y CN201321358 Y CN 201321358Y
- Authority
- CN
- China
- Prior art keywords
- variable displacement
- control
- pressure
- oil
- pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
- Control And Safety Of Cranes (AREA)
Abstract
The utility model discloses a crane hoist control system and a crane, wherein the crane hoist control system comprises a bidirectional variable pump, a bidirectional variable motor, an electro-hydraulic proportion control valve, an input device and a controller, wherein the two oil inlets of the bidirectional variable motor are respectively communicated with the two oil outlets of the bidirectional variable pump, and a hoist drum lifts a rope when the first oil inlet of the bidirectional variable motor is filled with liquid, and the hoist drum drops the rope when the second oil inlet of the bidirectional variable pump is filled with liquid, and the electro-hydraulic proportion control valve is connected with the bidirectional variable pump for controlling the action direction and displacement of output pressure oil of the bidirectional variable pump, the input device is used to input the command for controlling the hoist operation, the controller is used to receive the control command of the input device, and to output control signals for controlling the electro-hydraulic proportion control valve. The hydraulic impact and throttle loss can be avoided in the reversing process of the motor, thereby greatly increasing the service life of a hydraulic component and a pipeline, and assuring the system to have higher efficiency.
Description
Technical field
The utility model relates to technical field of engineering machinery, is specifically related to crane hoisting control system and hoisting crane.
Background technology
According to the difference of control principle, hydraulic control system can be divided into valve control system and pump control system.The crane hoisting system of existing fluid control adopts valve control system usually, as shown in Figure 1, utilize main multiple directional control valve 30 to control the direction and the speed of the object that hoists, when change-over valve 30 is in right position, HM Hydraulic Motor 60 is just being changeed and is being driven reel 20 lifting weight G by retarder 10, realizes that lift heavy rises; When change-over valve 30 was in position, a left side, HM Hydraulic Motor 60 was reversed and is driven reel 20 and transfers weight G, and realizing bearing a heavy burden descends, and at this moment, the balance cock 40 that hoists plays steady effect; When change-over valve 30 was in meta, the loop realized that load-bearing is static.Wherein, normally closed braking liquid cylinder pressure 70 is used to realize the braking of reel 20; On the branch road of brake cylinder, be provided with one-way throttle valve 50, braking liquid cylinder pressure 70 just thoroughly draws back brake block after guaranteeing the certain drive torque of HM Hydraulic Motor 60 generations, thereby can avoid before motor driven moment fully forms weight G slippery downwards, simultaneously, HM Hydraulic Motor 60 is after finishing heavy burden decline, and when promptly change-over valve 30 was replied metas, the check valve of valve 50 made the fluid of brake cylinder cavity of resorption discharge rapidly, guarantee the brake block snap catch, avoid weight G to continue to descend.
In the change-over valve commutation process,, not only can produce hydraulic efficiency impact, but also have the throttle loss of principle because liquid stream is obstructed suddenly during meta position or the commutation of right position left.Particularly for the large-tonnage hoisting crane, the problems referred to above show more obviously.
As everyone knows, when hydraulic efficiency impact takes place,, also can cause vibration equipment, produce very big noise because the pressure peak of moment than big several times of normal operation pressure, therefore all has damage effect to packing element, pipeline and Hydraulic Elements.When producing throttle loss, system's cal val is bigger, and therefore, although adopt permanent power and variable pump as propulsion source, The whole control system exists the problem that efficient reduces; In addition, behind the temperature build-up, the reduction of hydraulic oil liquid viscosity is let out increase in can causing, and then the uncontrollable weight downslide of the balance cock that causes hoisting, and has unsafe hidden danger.
Along with hoisting crane exploitation tonnage is increasing, based on the problem of existing hydraulic efficiency impact of valve control system and degradation of energy, the high efficiency of its crane hoisting hoisting system in urgent need to be improved and safe reliability.
The utility model content
At above-mentioned defective, the technical matters that the utility model solves is, a kind of crane hoisting control system and hoisting crane are provided.
The crane hoisting control system that the utility model provides comprises two way variable displacement pump, double-action variable displacement motor, electrohydraulic proportional control valve, input media and controller; Wherein, two oil inlets of described double-action variable displacement motor are communicated with two oil outlets of described two way variable displacement pump respectively, and during the first oil inlet feed liquor of this double-action variable displacement motor, the elevator reel is received rope; During the second oil inlet feed liquor of this double-action variable displacement motor, the elevator reel is put rope; Described electrohydraulic proportional control valve links to each other with described two way variable displacement pump, is used to control the action direction and the discharge capacity of two way variable displacement pump pressure oil output; Described input media is used to import the order of control elevator action; Described controller receives the control command of input media, and output is used to control the control signal of electrohydraulic proportional control valve.
Preferably, also comprise shuttle valve and pressure sensor; Wherein, two of described shuttle valve oil inlets are communicated with two oil outlets of described two way variable displacement pump respectively; Described pressure sensor is arranged on the fluid oil circuit of described shuttle valve, is used to gather the pressure signal of two way variable displacement pump pressure oil output and exports described controller to.Described controller comprises pre-value setup unit, calculating unit and comparing unit; Wherein, described pre-value setup unit is used to preestablish and store the relation table of corresponding relation between engine power and the rotating speed; Described calculating unit is used for according to the pressure signal and the rotating speed of two way variable displacement pump and the horsepower output that discharge capacity calculates described two way variable displacement pump that receive; Described comparing unit is used for the horsepower output of two way variable displacement pump and the comparing with the corresponding engine power of its rotating speed of pre-value setup unit that will calculate, if the horsepower output of described two way variable displacement pump is greater than engine power corresponding with it, then output reduces the control signal of described bidirectional variable pump capacity; If the horsepower output of described two way variable displacement pump is less than engine power corresponding with it, then output increases the control signal of described bidirectional variable pump capacity.
Preferably, also comprise tachogen, this tachogen is used to gather the tach signal of double-action variable displacement motor and exports described controller to; Described input media is a control handle, can be according to the variation output control signal corresponding of described control handle position; The calculating unit of described controller also is used for calculating according to the control signal that receives the theoretical rotational speed value of double-action variable displacement motor; The comparing unit of described controller also is used for the tach signal of the double-action variable displacement motor of described tachogen collection and theoretical rotational speed value are compared, if the tach signal of the double-action variable displacement motor of gathering is greater than the theoretical rotational speed value, then output reduces the control signal of described bidirectional variable pump capacity.
Preferably, when described controller output control signal was zero with the capacity reduction of two way variable displacement pump, if the tach signal of the double-action variable displacement motor that tachogen is gathered is greater than the theoretical rotational speed value, then output changed the control signal of described two way variable displacement pump pressure oil direction.
Preferentially, also comprise slippage pump, first balance cock, second balance cock and by pass valve; Wherein, first hydraulic fluid port of first balance cock and second balance cock all is communicated with the pressure oil outlet of described slippage pump; Second hydraulic fluid port of first balance cock and second balance cock is communicated with two oil outlets of described two way variable displacement pump respectively; Described by pass valve is arranged between the pressure oil outlet and fuel tank of described slippage pump.
Preferably, also comprise the repairing check valve, its oil inlet is communicated with the pressure oil outlet of described slippage pump, and its oil outlet is communicated with second oil inlet of described double-action variable displacement motor.
Preferably, also comprise single-acting brake cylinder and solenoid directional control valve; Described single-acting brake cylinder is used to control normally closed brake; Described solenoid directional control valve has two control positioies, be in position, a left side during this solenoid directional control valve dead electricity, the rod chamber of described single-acting brake cylinder is communicated with fuel tank, and this solenoid directional control valve gets and is in right position when electric, and the rod chamber of described single-acting brake cylinder exports with the pressure oil of slippage pump and is communicated with.
Preferably, also comprise pressure relay, be arranged on the feed liquor oil circuit of double-action variable displacement motor second oil inlet, when the inlet hydraulic of double-action variable displacement motor second oil inlet during less than the operation pressure of this pressure relay, output signal to the control signal receiving end of described solenoid directional control valve, described solenoid directional control valve dead electricity.
Preferably, described controller also comprises memory cell, is used to store the maximum pressure signal that pressure sensor is gathered when promoting; When weight aloft needs to promote once more or descends, the comparing unit of described controller compares the maximum pressure signal of storing in the pressure signal of pressure sensor collection and the memory cell, if the pressure signal of gathering is during greater than the maximum pressure signal stored in the memory cell, output control signals to solenoid directional control valve, described solenoid directional control valve gets.
The crane hoisting control system that the utility model provides adopts two way variable displacement pump and double-action variable displacement motor to constitute pump control system.In working order down, the operator handles the order that input media sends the action of control elevator according to action need, described controller receives the control command of input media and outputs control signals to electrohydraulic proportional control valve, with the action direction and the discharge capacity of control two way variable displacement pump pressure oil output, thereby, system can satisfy the pressure oil liquid that uses needs for providing.
Because the technical solution of the utility model is directly utilized the rotation direction and the speed of two way variable displacement pump control double-action variable displacement motor, compare with existing valve control system, control system described in the utility model does not have hydraulic efficiency impact in the motor commutation process, therefore, can improve the service life of Hydraulic Elements and pipeline greatly, reduce the complete machine maintenance cost; In addition, do not have the throttle loss of control cock generation in the control system described in the utility model, thereby avoided the throttle loss of existing valve control system, therefore, the system that can guarantee has higher efficient.
In the preferred version of the present utility model, be provided with shuttle valve between two oil outlets of described two way variable displacement pump, the fluid oil circuit of described shuttle valve is provided with pressure sensor; Because two oil inlets of described shuttle valve are communicated with two oil outlets of two way variable displacement pump respectively, like this, the pressure of shuttle valve oil outlet is always system works pressure.Down, described pressure sensor can detect the force value that two way variable displacement pump exports the pressure oil liquid of system in real time in working order, and exports this pressure signal to described controller; The horsepower output that described controller calculates described two way variable displacement pump according to the rotating speed and the discharge capacity of this pressure signal and pump, and this horsepower output and the predefined and cooresponding engine power of this rotating speed compared, if the horsepower output of described two way variable displacement pump is greater than engine power corresponding with it, then export control signal to reduce described bidirectional variable capacity of pump, thereby improve system works efficient, guarantee driving engine and hydraulic efficiency pressure system co-ordination.
In another preferred version of the present utility model, also comprise the tachogen that is used to gather the double-action variable displacement motor tach signal; The calculating unit of described controller calculates the theoretical rotational speed value of double-action variable displacement motor according to the control signal that receives; The comparing unit of described controller compares the tach signal and the theoretical rotational speed value of the double-action variable displacement motor of described tachogen collection, if the tach signal of the double-action variable displacement motor of gathering is greater than the theoretical rotational speed value, then output reduces the control signal of described bidirectional variable pump capacity, to eliminate the stall phenomenon.Further, when if described controller output control signal is zero with the capacity reduction of two way variable displacement pump, also do not eliminate the stall phenomenon, then controller output changes the control signal of described two way variable displacement pump pressure oil direction, at this moment, the reverse fuel feeding of two way variable displacement pump carries out the absorption of power as automatically controlled balance cock.
Operating mode is downloaded in heavy burden at hoisting crane, and the feed liquor oil circuit of another preferred version double-action variable displacement motor second oil inlet of the present utility model is provided with pressure relay, is used to detect the input pressure of this mouthful; And adopt the mode of operation of solenoid directional control valve control brake oil cylinder.During normality, described solenoid directional control valve is in position, a left side, and the rod chamber of described single acting oil cylinder is communicated with fuel tank, i.e. braking mode; When hoisting crane was in normal operation, described solenoid directional control valve got the electric right position that is in, and the rod chamber of described single-acting brake cylinder is communicated with promptly non-braking mode with the outlet of the pressure oil of slippage pump.When hoisting crane heavy burden stall, the discharge capacity of double-action variable displacement motor increases, the inlet hydraulic of its second oil inlet is less than the operation pressure of this pressure relay, at this moment, pressure relay outputs signal to the control signal receiving end of described solenoid directional control valve, described solenoid directional control valve dead electricity, this solenoid directional control valve dead electricity, brake by force by brake cylinder, thus the potential safety hazard of having avoided stall to bring.
Another preferred version of the present utility model has the function that prevents that secondary from gliding, and described controller also comprises the memory cell that is used to store the maximum pressure signal that pressure sensor is gathered when promoting; When weight aloft needed to promote once more or descends, if the pressure signal of gathering during greater than the maximum pressure signal stored in the memory cell, outputs control signals to solenoid directional control valve, described electromagnetic valve got; That is,, when having only system pressure to be enough to make motor have to overcome the drive torque of weight, just open drg if during restarting.
The utility model also provides a kind of hoisting crane, has the control system of control elevator operation, and the control system of described control elevator operation adopts foregoing crane hoisting control system.
Description of drawings
Fig. 1 is the hydraulic schematic diagram of existing valve control crane hoisting control system;
Fig. 2 is the hydraulic schematic diagram of crane hoisting control system described in the utility model;
Fig. 3 is the control unit block diagram of crane hoisting control system described in the utility model.
Among Fig. 2-Fig. 3:
Two way variable displacement pump 1, double-action variable displacement motor 2, electrohydraulic proportional control valve 3, input media 4, controller 5, pre-value setup unit 51, calculating unit 52, comparing unit 53, memory cell 54, shuttle valve 6, pressure sensor 7, tachogen 8, slippage pump 9, first balance cock 11, second balance cock 12, by pass valve 13, repairing check valve 14, brake cylinder 15, solenoid directional control valve 16, pressure relay 17, energy storage 18.
The specific embodiment
Core of the present utility model is need not control cock, directly utilize the direction of two way variable displacement pump pressure oil output and rotation direction and the speed that discharge capacity is controlled double-action variable displacement motor, in the working process, can avoid the generation of hydraulic efficiency impact and throttle loss, thereby improve the service life of Hydraulic Elements and pipeline, guarantee that system has higher efficient.
Specify present embodiment below in conjunction with Figure of description.
The crane hoisting control system that the utility model provides comprises two way variable displacement pump 1, double-action variable displacement motor 2, electrohydraulic proportional control valve 3, input media 4 and controller 5.
Referring to Fig. 2, this figure is the hydraulic schematic diagram of crane hoisting control system described in the utility model.
As shown in Figure 2, two oil inlets of double-action variable displacement motor 2 are communicated with two oil outlets of described two way variable displacement pump 1 respectively, and during the first oil inlet A feed liquor of this double-action variable displacement motor 2, elevator reel (not shown) is received rope, realizes the crane hoisting operation; During the second oil inlet B feed liquor of this double-action variable displacement motor 2, the elevator reel is put rope, realizes hoisting crane decline operation.
Electrohydraulic proportional control valve 3 links to each other with described two way variable displacement pump 1, is used to control the action direction and the discharge capacity of two way variable displacement pump 1 pressure oil output; Thereby the rotation direction and the rotating speed of control double-action variable displacement motor 2.
Referring to Fig. 3, this figure is the control unit block diagram of crane hoisting control system described in the utility model.
As shown in Figure 3, input media 4 is used to import the order of control elevator action; Controller 5 receives the control command of input media 4, and output is used to control the control signal of electrohydraulic proportional control valve 3.Particularly, described input media 4 is a control handle, be built-in with two two-way angle sensors, can export corresponding pulse-width modulation control signal according to the variation of described control handle position, controller 5 carries out this signal to export electrohydraulic proportional control valve 3 to after the processing and amplifying, the pilot pressure oil delivery pressure of control electrohydraulic proportional control valve 3, thereby the discharge capacity of control two way variable displacement pump 1.
For the horsepower output of better controlling two way variable displacement pump and the power that starts are complementary, improve the efficient of system, further, the utility model also comprises shuttle valve 6 and pressure sensor 7.
Two oil inlets of shuttle valve 6 are communicated with two oil outlets of described two way variable displacement pump 1 respectively; Described pressure sensor 7 is arranged on the fluid oil circuit of described shuttle valve 6, is used to gather the pressure signal of two way variable displacement pump 1 pressure oil output and exports described controller 5 to.Because pressure sensor 7 is communicated with the liquid outlet of described shuttle valve 6, therefore, the pressure signal that this pressure sensor 7 is gathered is always operation pressure.
As shown in Figure 3, described controller 5 comprises pre-value setup unit 51, calculating unit 52 and comparing unit 53; Wherein, described pre-value setup unit 51 is used to preestablish and store the relation table of corresponding relation between engine power and the rotating speed; Described calculating unit 52 is used for according to the pressure signal and the rotating speed of two way variable displacement pump 1 and the horsepower output that discharge capacity calculates described two way variable displacement pump 1 that receive; Described comparing unit 53 is used for the horsepower output of two way variable displacement pump 1 and the comparing with the corresponding engine power of its rotating speed of pre-value setup unit 51 that will calculate, if the horsepower output of described two way variable displacement pump 1 is greater than engine power corresponding with it, then output reduces the control signal of described bidirectional variable pump capacity; If the horsepower output of described two way variable displacement pump 1 is less than engine power corresponding with it, then output increases the control signal of described bidirectional variable pump capacity, is complementary with horsepower output and the engine power of guaranteeing two way variable displacement pump 1.
Occur the stall phenomenon for preventing that hoisting mechanism from bearing a heavy burden at hoisting crane when descending, further, the utility model also comprises tachogen 8, and this tachogen 8 is used to gather the tach signal of double-action variable displacement motor 2 and exports described controller 5 to; The calculating unit 52 of described controller 1 also is used for calculating according to the control signal that receives the theoretical rotational speed value of double-action variable displacement motor 2; The comparing unit 53 of described controller 5 also is used for the tach signal and the theoretical rotational speed value of the double-action variable displacement motor 2 of described tachogen 8 collections are compared, if the tach signal of the double-action variable displacement motor of gathering 2 is greater than the theoretical rotational speed value, then output reduces the control signal of described bidirectional variable pump capacity, to reduce the oil absorption of double-action variable displacement motor, avoid the existing potential safety hazard of stall.Further, when described controller 5 output control signals are zero with the capacity reduction of two way variable displacement pump 1, if the tach signal of the double-action variable displacement motor 2 that tachogen 8 is gathered is greater than the theoretical rotational speed value, then output changes the control signal of described two way variable displacement pump pressure oil direction.
Oil liquid leakage is constantly arranged at work,, keep system's normal operation, in time replenish fluid must for system in order to replenish the consumption of these leakages.Further, the utility model also comprises discharge capacity and the pressure slippage pump 9 less than main pump, is used to select first balance cock 11 and second balance cock 12 and the by pass valve 13 of repairing direction.The slippage pump 8 that replenishes fluid for system can increase main pump 1 oil inlet place pressure, produces cavitation erosion when preventing big flow, to avoid letting out in the system two way variable displacement pump 1 emptying phenomenon of being brought, improves work life.
Wherein, first hydraulic fluid port of first balance cock 11 and second balance cock 12 all is communicated with the pressure oil outlet of described slippage pump 9; Second hydraulic fluid port of first balance cock 11 and second balance cock 12 is communicated with two oil outlets of described two way variable displacement pump 1 respectively, with low pressure side repairing to working connection, and the flow that compensation is leaked owing to pump, motor volumetric loss.
Described by pass valve 13 is arranged between the pressure oil outlet and fuel tank of described slippage pump 9, prevents pump and two way variable displacement pump 1 overload.
In addition, also comprise repairing check valve 14, its oil inlet is communicated with the pressure oil outlet of described slippage pump 9, its oil outlet is communicated with second oil inlet of described double-action variable displacement motor 2, for avoiding the stall of hoisting crane motor that additional fluid is provided, guarantee that the weight descending speed is steadily reliable, improve the safety of operation.
In hoisting crane heavy burden decline operating mode, if stall occurs than serious situation, slippage pump 9 can't provide the additional fluid of meet requirements.Further, the utility model also comprises single-acting brake cylinder 15 and solenoid directional control valve 16; Described single-acting brake cylinder 15 is used to control the normally closed brake (not shown); Described solenoid directional control valve 16 has two control positioies, is in position, a left side during these solenoid directional control valve 16 dead electricity, and the rod chamber of described single-acting brake cylinder 15 is communicated with fuel tank, i.e. braking mode; This solenoid directional control valve 16 be in right position when electric, the rod chamber of described single-acting brake cylinder 15 exports with the pressure oil of slippage pump 9 and is communicated with promptly non-braking mode.
As shown in Figure 2, also comprise energy storage 18, its oil inlet is communicated with the pressure oil outlet of described slippage pump 9, with stored energy, elimination pulsation.
As shown in Figure 3, described controller 5 also comprises memory cell 54, is used to store the maximum pressure signal that pressure sensor 7 is gathered when promoting; When weight aloft needs to promote once more or descends, the maximum pressure signal of storing in the pressure signal that the comparing unit 53 of described controller 5 is gathered pressure sensor 7 and the memory cell 54 compares, if the pressure signal of gathering is during greater than the maximum pressure signal of storage in the memory cell 54, output control signals to solenoid directional control valve 16, described solenoid directional control valve 16.When weight aloft needed to promote once more or descends, the maximum pressure that system pressure must reach memory storage could move, and when promptly having only system pressure to be enough to make motor have to overcome the drive torque of weight, just opened the single acting oil cylinder brake off; When weight lands, manually or automatically remove memory value.
Special version be; parts such as two way variable displacement pump 1 described in the utility model, shuttle valve 6, first balance cock 11, second balance cock 12 and by pass valve 13 can integratedly design; to obtain better matching performance and assembly process process, use needs all in the protection domain of this patent as long as satisfy.
Present embodiment also provides a kind of hoisting crane, has the control system of control elevator operation, and the control system of described control elevator operation adopts foregoing crane hoisting control system.
The above only is a preferred implementation of the present utility model; should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the utility model principle; can also make some improvements and modifications, these improvements and modifications also should be considered as protection domain of the present utility model.
Claims (10)
1, the crane hoisting control system is characterized in that, comprising:
Two way variable displacement pump;
Double-action variable displacement motor, two oil inlet are communicated with two oil outlets of described two way variable displacement pump respectively, and during the first oil inlet feed liquor of this double-action variable displacement motor, the elevator reel is received rope; During the second oil inlet feed liquor of this double-action variable displacement motor, the elevator reel is put rope;
Electrohydraulic proportional control valve links to each other with described two way variable displacement pump, is used to control the action direction and the discharge capacity of two way variable displacement pump pressure oil output;
Input media is used to import the order of control elevator action; With
Controller receives the control command of input media, and exports the control signal that is used to control electrohydraulic proportional control valve.
2, crane hoisting control system according to claim 1 is characterized in that, also comprises:
Shuttle valve, two oil inlet are communicated with two oil outlets of described two way variable displacement pump respectively; With
Pressure sensor is arranged on the fluid oil circuit of described shuttle valve, is used to gather the pressure signal of two way variable displacement pump pressure oil output and exports described controller to; And described controller comprises:
The pre-value setup unit is used to preestablish and store the relation table of corresponding relation between engine power and the rotating speed;
Calculating unit is used for according to the pressure signal and the rotating speed of two way variable displacement pump and the horsepower output that discharge capacity calculates described two way variable displacement pump that receive; With
Comparing unit, be used for the horsepower output of two way variable displacement pump and the comparing of pre-value setup unit that to calculate with the corresponding engine power of its rotating speed, if the horsepower output of described two way variable displacement pump is greater than engine power corresponding with it, then output reduces the control signal of described bidirectional variable pump capacity; If the horsepower output of described two way variable displacement pump is less than engine power corresponding with it, then output increases the control signal of described bidirectional variable pump capacity.
3, crane hoisting control system according to claim 2 is characterized in that, also comprises:
Tachogen is used to gather the tach signal of double-action variable displacement motor and exports described controller to; And
Described input media is a control handle, can be according to the variation output control signal corresponding of described control handle position; And
The calculating unit of described controller also is used for calculating according to the control signal that receives the theoretical rotational speed value of double-action variable displacement motor; The comparing unit of described controller also is used for the tach signal of the double-action variable displacement motor of described tachogen collection and theoretical rotational speed value are compared, if the tach signal of the double-action variable displacement motor of gathering is greater than the theoretical rotational speed value, then output reduces the control signal of described bidirectional variable pump capacity.
4, crane hoisting control system according to claim 3, it is characterized in that, when described controller output control signal is zero with the capacity reduction of two way variable displacement pump, if the tach signal of the double-action variable displacement motor that tachogen is gathered is greater than the theoretical rotational speed value, then output changes the control signal of described two way variable displacement pump pressure oil direction.
5, crane hoisting control system according to claim 3 is characterized in that, also comprises:
Slippage pump;
First balance cock and second balance cock, both first hydraulic fluid ports all are communicated with the pressure oil outlet of described slippage pump; Both second hydraulic fluid ports are communicated with two oil outlets of described two way variable displacement pump respectively; With
By pass valve is arranged between the pressure oil outlet and fuel tank of described slippage pump.
6, crane hoisting control system according to claim 5 is characterized in that, also comprises:
The repairing check valve, its oil inlet is communicated with the pressure oil outlet of described slippage pump, and its oil outlet is communicated with second oil inlet of described double-action variable displacement motor.
7, crane hoisting control system according to claim 5 is characterized in that, also comprises:
The single-acting brake cylinder is used to control normally closed brake; With
Solenoid directional control valve, have two control positioies, be in position, a left side during this solenoid directional control valve dead electricity, the rod chamber of described single-acting brake cylinder is communicated with fuel tank, this solenoid directional control valve gets and is in right position when electric, and the rod chamber of described single-acting brake cylinder exports with the pressure oil of slippage pump and is communicated with.
8, crane hoisting control system according to claim 7 is characterized in that, also comprises:
Pressure relay, be arranged on the feed liquor oil circuit of double-action variable displacement motor second oil inlet, when the inlet hydraulic of double-action variable displacement motor second oil inlet during, output signal to the control signal receiving end of described solenoid directional control valve, described solenoid directional control valve dead electricity less than the operation pressure of this pressure relay.
9, crane hoisting control system according to claim 7 is characterized in that, described controller also comprises memory cell, is used to store the maximum pressure signal that pressure sensor is gathered when promoting; When weight aloft needs to promote once more or descends, the comparing unit of described controller compares the maximum pressure signal of storing in the pressure signal of pressure sensor collection and the memory cell, if the pressure signal of gathering is during greater than the maximum pressure signal stored in the memory cell, output control signals to solenoid directional control valve, described solenoid directional control valve gets.
10, hoisting crane has the control system of control elevator operation, it is characterized in that the control system of described control elevator operation adopts as the described crane hoisting control system of arbitrary claim in the claim 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201791664U CN201321358Y (en) | 2008-11-25 | 2008-11-25 | Crane hoist control system and crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201791664U CN201321358Y (en) | 2008-11-25 | 2008-11-25 | Crane hoist control system and crane |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201321358Y true CN201321358Y (en) | 2009-10-07 |
Family
ID=41158745
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008201791664U Expired - Lifetime CN201321358Y (en) | 2008-11-25 | 2008-11-25 | Crane hoist control system and crane |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201321358Y (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101734565B (en) * | 2008-11-25 | 2011-04-06 | 徐州重型机械有限公司 | Crane and winch control system thereof |
| CN102153027A (en) * | 2011-04-12 | 2011-08-17 | 武汉船用机械有限责任公司 | Stepless regulation constant tension device for hydraulic winch |
| CN102815633A (en) * | 2012-09-03 | 2012-12-12 | 上海中联重科桩工机械有限公司 | Control device for hydraulic winch and engineering machine |
| CN103112782A (en) * | 2013-02-28 | 2013-05-22 | 徐工集团工程机械股份有限公司 | Synchronous control device and method of multi-winch system |
| CN103482478A (en) * | 2013-10-17 | 2014-01-01 | 徐工集团工程机械股份有限公司 | Method and device for identifying swinging characteristic of crane hook |
| CN103588134A (en) * | 2012-08-14 | 2014-02-19 | 徐工集团工程机械股份有限公司 | Hoist control device in open hydraulic system for crane |
| CN103613011A (en) * | 2013-11-28 | 2014-03-05 | 徐州重型机械有限公司 | Autonomous control system for crane |
| CN104944288A (en) * | 2015-05-13 | 2015-09-30 | 徐州重型机械有限公司 | Crane winch motor pressure memory control system and method |
| CN105217504A (en) * | 2015-10-27 | 2016-01-06 | 中国矿业大学 | A kind of mining hydraulic winch electro-hydraulic proportional control system |
| CN105927601A (en) * | 2016-05-19 | 2016-09-07 | 武汉船用机械有限责任公司 | Promotion hydraulic system |
| CN109896461A (en) * | 2019-03-29 | 2019-06-18 | 北京航天发射技术研究所 | A kind of high reliability and safety big load hoist braking system and method |
| CN110980529A (en) * | 2019-12-30 | 2020-04-10 | 浙江三一装备有限公司 | Crane hydraulic control system and crane |
| CN111305004A (en) * | 2020-02-24 | 2020-06-19 | 三一汽车制造有限公司 | Traveling machine, and travel brake system and travel brake method for traveling machine |
| CN114314401A (en) * | 2022-03-07 | 2022-04-12 | 徐州徐工基础工程机械有限公司 | Closed type winch emergency brake control system, equipment and method |
-
2008
- 2008-11-25 CN CNU2008201791664U patent/CN201321358Y/en not_active Expired - Lifetime
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101734565B (en) * | 2008-11-25 | 2011-04-06 | 徐州重型机械有限公司 | Crane and winch control system thereof |
| CN102153027A (en) * | 2011-04-12 | 2011-08-17 | 武汉船用机械有限责任公司 | Stepless regulation constant tension device for hydraulic winch |
| CN103588134B (en) * | 2012-08-14 | 2015-08-19 | 徐工集团工程机械股份有限公司 | Winch control device in hoisting crane open type hydraulic system |
| CN103588134A (en) * | 2012-08-14 | 2014-02-19 | 徐工集团工程机械股份有限公司 | Hoist control device in open hydraulic system for crane |
| CN102815633A (en) * | 2012-09-03 | 2012-12-12 | 上海中联重科桩工机械有限公司 | Control device for hydraulic winch and engineering machine |
| CN102815633B (en) * | 2012-09-03 | 2015-04-22 | 上海中联重科桩工机械有限公司 | Control device for hydraulic winch and engineering machine |
| CN103112782A (en) * | 2013-02-28 | 2013-05-22 | 徐工集团工程机械股份有限公司 | Synchronous control device and method of multi-winch system |
| CN103482478A (en) * | 2013-10-17 | 2014-01-01 | 徐工集团工程机械股份有限公司 | Method and device for identifying swinging characteristic of crane hook |
| CN103482478B (en) * | 2013-10-17 | 2015-11-25 | 徐工集团工程机械股份有限公司 | Crane hook rocking feature discrimination method and device |
| CN103613011B (en) * | 2013-11-28 | 2015-07-22 | 徐州重型机械有限公司 | Autonomous control system for crane |
| CN103613011A (en) * | 2013-11-28 | 2014-03-05 | 徐州重型机械有限公司 | Autonomous control system for crane |
| CN104944288A (en) * | 2015-05-13 | 2015-09-30 | 徐州重型机械有限公司 | Crane winch motor pressure memory control system and method |
| CN105217504A (en) * | 2015-10-27 | 2016-01-06 | 中国矿业大学 | A kind of mining hydraulic winch electro-hydraulic proportional control system |
| CN105927601A (en) * | 2016-05-19 | 2016-09-07 | 武汉船用机械有限责任公司 | Promotion hydraulic system |
| CN109896461A (en) * | 2019-03-29 | 2019-06-18 | 北京航天发射技术研究所 | A kind of high reliability and safety big load hoist braking system and method |
| CN110980529A (en) * | 2019-12-30 | 2020-04-10 | 浙江三一装备有限公司 | Crane hydraulic control system and crane |
| CN111305004A (en) * | 2020-02-24 | 2020-06-19 | 三一汽车制造有限公司 | Traveling machine, and travel brake system and travel brake method for traveling machine |
| CN114314401A (en) * | 2022-03-07 | 2022-04-12 | 徐州徐工基础工程机械有限公司 | Closed type winch emergency brake control system, equipment and method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101734565B (en) | Crane and winch control system thereof | |
| CN201321358Y (en) | Crane hoist control system and crane | |
| KR930002505B1 (en) | Hydraulic lift mechanism | |
| CN100427771C (en) | Energy saving hydraulic lifting system of variable hydraulic counterweight | |
| CN101709725B (en) | Downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique | |
| CN200974743Y (en) | Energy-saving tower machine hydraulic stepless change control system | |
| CN103950870B (en) | A kind of forklift hydraulic system of double pump fuel feeding band energy regenerating | |
| CN202575822U (en) | Engineering machinery and hoisting hydraulic control system thereof | |
| CN108083116B (en) | Hydraulic control system for crane | |
| CN102153027A (en) | Stepless regulation constant tension device for hydraulic winch | |
| CN201526546U (en) | Hydraulic control system of underground anti-explosion hoister adopting multi-pump combination technique | |
| CN110027984B (en) | Hydraulic system of large-load hoister | |
| CN103470544A (en) | Energy-saving hoisting system of hydraulic crane | |
| CN203754318U (en) | Crane winching hydraulic system and crane | |
| CN102616705A (en) | Energy-saving forklift hydraulic system with energy recovery function | |
| CN201132745Y (en) | Hydraulic lifting device for column crane | |
| CN103883573A (en) | Hydraulic boom control system and harbor handling machine | |
| CN102628465A (en) | Energy recovery type lifting hydraulic system for hoisting and conveying machine | |
| CN108953309B (en) | Energy recovery and recycling hydraulic system | |
| CN203717497U (en) | Cantilever crane hydraulic control system and harbor handling machinery | |
| CN104865083A (en) | Multi-rope friction hoist load simulation hydraulic loading device | |
| CN102606131B (en) | Hydraulically-driven top drive control system | |
| WO2010123378A1 (en) | Recycling of energy | |
| CN202545431U (en) | Energy recycling-type hoisting hydraulic system for hoisting and conveying machinery | |
| CN111395439B (en) | Excavator movable arm-rotation closed hydraulic system and control method |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20091007 Effective date of abandoning: 20081125 |