CN102491173B - Crane and closed type hoisting negative power control system for crane - Google Patents
Crane and closed type hoisting negative power control system for crane Download PDFInfo
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- CN102491173B CN102491173B CN201110412215.0A CN201110412215A CN102491173B CN 102491173 B CN102491173 B CN 102491173B CN 201110412215 A CN201110412215 A CN 201110412215A CN 102491173 B CN102491173 B CN 102491173B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/20—Control systems or devices for non-electric drives
Abstract
The invention provides a crane and a closed type hoisting negative power control system for the crane, which are used for solving the problem of poor effect of the closed type hoisting negative power control system for the crane in the prior art. The control system comprises an engine, a transfer case, an open type system and a closed type system, wherein the open type system and the closed type system are connected with the transfer case respectively, and are connected to the engine through the transfer case; the closed type system comprises a closed type variable pump connected with the transfer case, a hoisting motor connected with the closed type variable pump through a hydraulic pipeline, and a hoisting speed reducer connected with the hoisting motor; and the transfer case is used for transmitting a part of or all negative power to the open type system during descending operation of the crane. Due to the adoption of the technical scheme of the invention, negative power produced during closed type hoisting descending is transferred to the open type system through the transfer case and is absorbed by the open type system, the descending speed of a heavy object is not limited, and a good control effect is achieved.
Description
Technical field
The present invention relates to technical field of engineering machinery, relate to especially a kind of hoisting crane and closed type hoisting negative power control system for crane.
Background technology
Hoisting crane is a kind of common construction machinery and equipment.In correlation technique, by engine drive open type or closed system, to realize hoisting of lift heavy thing, in this closed system, mainly comprise controllable capacity pump and hoist motor.
The speed that weight declines in open-circuit system can regulate control by balance cock, and in closed system because closed system radiating effect is poor, therefore balance cock can not be installed.Negative power absorption pattern in correlation technique mainly absorbs a part of negative power by driving engine itself, and its principle as shown in Figure 1.Fig. 1 is the schematic diagram by closed type hoisting negative power absorption pattern principle according to the hoisting crane in correlation technique.Arrow in Fig. 1 represents the flow of power, the lift heavy thing that weight G is hoisting crane.As shown in Figure 1, when weight G declines, produce negative power, this negative power passes to closed system, and closed system is to engine output, correspondingly driving engine absorbed power.
In correlation technique, can only limit by the descending speed of restriction weight the generation of negative power.Development along with Crane Industry, hoisting capacity is increasing, the negative power that need to absorb during decline is more and more (because size and the weight quality of negative power are directly proportional) also, speed is confined also more and more less, because the absorbent negative power of driving engine itself is limited, have driving danger after exceeding the absorption region of driving engine.Therefore the poor effect of controlling with closed type hoisting negative power for hoisting crane in correlation technique, for this problem, not yet proposes effective solution in correlation technique.
Summary of the invention
Main purpose of the present invention is to provide a kind of hoisting crane and closed type hoisting negative power control system for crane, to solve the problem of the poor effect of controlling with closed type hoisting negative power for hoisting crane in prior art.
To achieve these goals, according to an aspect of the present invention, provide a kind of closed type hoisting negative power control system for crane.
The negative power that closed type hoisting negative power control system for crane of the present invention produces when lift heavy thing is transferred for absorbing the hoisting mechanism of hoisting crane, described control system comprises driving engine, auxiliary gear box, open-circuit system and closed system, wherein: described open-circuit system is connected with described auxiliary gear box respectively with closed system, and is connected to described driving engine by described auxiliary gear box; Described closed system comprises the enclosed controllable capacity pump being connected with described auxiliary gear box, the hoist motor being connected with described enclosed controllable capacity pump by hydraulic tubing and the hoisting speed reducer being connected with described hoist motor; Described auxiliary gear box for partly or entirely passing to described open-circuit system by described negative power when hoisting crane declines operation.
Further, described open-circuit system comprises: open type controllable capacity pump, is connected with described auxiliary gear box, for obtaining power pressure oil output from described auxiliary gear box; Proportional reversing valve, is connected with described open type controllable capacity pump; The loading by pass valve of described hoisting crane, is connected with described proportional reversing valve; Guide proportion reducing valve, is connected with described proportional reversing valve, for controlling described pressure oil, flows to the flow of described loading by pass valve via described proportional reversing valve.
Further, described open-circuit system comprises: open type controllable capacity pump, is connected with described auxiliary gear box, for obtaining power pressure oil output from described auxiliary gear box; Pilot operated directional control valve, is connected with described open type controllable capacity pump; Ratio loads by pass valve, is connected with described pilot operated directional control valve; Solenoid directional control valve, is connected with described pilot operated directional control valve, for controlling conducting or the shutoff of described pilot operated directional control valve.
Further, described open-circuit system comprises: open type controllable capacity pump, is connected with described auxiliary gear box, for obtaining power pressure oil output from described auxiliary gear box; The first and second proportional reversing valves, are all connected with described open type controllable capacity pump; First to fourth guide proportion reducing valve, wherein the first and second guide proportion reducing valves are connected with the first proportional reversing valve, and the third and fourth guide proportion reducing valve is connected with the second proportional reversing valve; Hydraulic Elements and loading by pass valve, the first hydraulic fluid port of wherein said Hydraulic Elements is connected with described the first and second proportional reversing valves, and the second hydraulic fluid port is connected with described the first proportional reversing valve, and described loading by pass valve is connected with described the second proportional reversing valve; And described Hydraulic Elements are for absorbing the power that described open type controllable capacity pump is obtained; Described the first guide proportion reducing valve flows to the flow of the first hydraulic fluid port of described Hydraulic Elements for controlling described pressure oil via described the first proportional reversing valve; Described the second guide proportion reducing valve flows to the flow of the second hydraulic fluid port of described Hydraulic Elements for controlling described pressure oil via described the first proportional reversing valve; Described the 3rd guide proportion reducing valve flows to the flow of the first hydraulic fluid port of described Hydraulic Elements for controlling described pressure oil via described the second proportional reversing valve; Described the 4th guide proportion reducing valve flows to the flow of described loading by pass valve for controlling described pressure oil via described the second proportional reversing valve.
Further, described loading by pass valve is that ratio loads by pass valve.
Further, described Hydraulic Elements are that HM Hydraulic Motor or two plate valves that two plate valve interflow are controlled collaborate the telescopic oil cylinder of controlling.
Further, the amplitude oil cylinder that described Hydraulic Elements are described hoisting crane, the rodless cavity that described the first hydraulic fluid port is this amplitude oil cylinder, the rod chamber that described the second hydraulic fluid port is this amplitude oil cylinder.
Further, described amplitude oil cylinder is two amplitude oil cylinder.
Further, described open type controllable capacity pump is Load sensing pump or automatically controlled controllable capacity pump.
According to another aspect of the invention, provide a kind of hoisting crane, this hoisting crane comprises closed type hoisting negative power control system for crane of the present invention.
Apply technical scheme of the present invention, can obtain following beneficial effect:
The negative power producing when 1, enclosed elevator declines is delivered to open-circuit system by auxiliary gear box, by open-circuit system, is absorbed, and weight descending speed is no longer restricted;
2, by controlling the electric current of guide proportion reducing valve, realize proportional reversing valve and export to the flow proportional that ratio loads by pass valve and control, to obtain ratio, load the different loading power of by pass valve, owing to controlling as step-less adjustment, therefore load and stablize, can not make speed produce sudden change;
3, the pressure that ratio loads by pass valve also can step-less adjustment, and the negative power producing in closed system is little compared with low system overshoot compared with hour setting pressure, load more steady, when the negative power of closed system generation is larger, the higher satisfied loading power requirement of setting pressure;
4, how the negative power that no matter closed system is exported changes, and the pressure that all can load by pass valve by electric current or the ratio of control guide proportion reducing valve make the power of driving engine maintain target control value;
5, by a proportional reversing valve, realize amplitude-variation hoisting and two functions of system loads, more traditional mode has been saved a proportional reversing valve.
Accompanying drawing explanation
Figure of description is used to provide a further understanding of the present invention, forms the application's a part, and schematic description and description of the present invention is used for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the schematic diagram by closed type hoisting negative power absorption pattern principle according to the hoisting crane in correlation technique;
Fig. 2 is the schematic diagram of the power transitive relation during according to the engine output of the embodiment of the present invention;
Fig. 3 is the schematic diagram of the power transitive relation during according to the driving engine absorbed power of the embodiment of the present invention;
Fig. 4 is the first basic structure schematic diagram according to the closed type hoisting negative power control system for crane of the embodiment of the present invention;
Fig. 5 is the second basic structure schematic diagram according to the closed type hoisting negative power control system for crane of the embodiment of the present invention;
Fig. 6 is the third basic structure schematic diagram according to the closed type hoisting negative power control system for crane of the embodiment of the present invention;
Fig. 7 is according to the 4th of the closed type hoisting negative power control system for crane of the embodiment of the present invention the kind of basic structure schematic diagram.
The specific embodiment
It should be noted that, in the situation that not conflicting, embodiment and the feature in embodiment in the application can combine mutually.Describe below with reference to the accompanying drawings and in conjunction with the embodiments the present invention in detail.
The closed type hoisting negative power control system for crane of the embodiment of the present invention is mainly used in absorbing the negative power that the hoisting mechanism of hoisting crane produces when lift heavy thing is transferred.Fig. 2 is the schematic diagram of the power transitive relation during according to the engine output of the embodiment of the present invention.Fig. 3 is the schematic diagram of the power transitive relation during according to the driving engine absorbed power of the embodiment of the present invention.
As shown in Figures 2 and 3, the closed type hoisting negative power control system for crane of the embodiment of the present invention mainly comprises driving engine 1, auxiliary gear box 2, open-circuit system 3 and closed system 4.Wherein open-circuit system 3 is connected with auxiliary gear box 2 respectively with closed system 4, and is connected to driving engine 1 by auxiliary gear box 2.Closed system 4 comprises interconnective enclosed controllable capacity pump and hoist motor, also comprises hoisting speed reducer (not shown).Auxiliary gear box 2 can be used in when hoisting crane rises operation the power of driving engine output is passed to open-circuit system 3 and closed system 4 (as shown in Figure 3, wherein arrow represents power flow direction), control aspect for negative power, auxiliary gear box 2 can be when hoisting crane declines operation by the part of negative power (now another part passes to driving engine) or all pass to open-circuit system 3 (as shown in Figure 3, wherein arrow represents power flow direction).Fig. 3 also shows weight G, and this weight G produces negative power when declining.
Fig. 4 is the first basic structure schematic diagram according to the closed type hoisting negative power control system for crane of the embodiment of the present invention.As shown in Figure 4, the optional structure of the first of the open-circuit system 3 in closed type hoisting negative power control system for crane is to comprise: open type controllable capacity pump 30, is connected with auxiliary gear box 2, for obtain power pressure oil output from auxiliary gear box; Proportional reversing valve 41; The loading by pass valve 43 of guide proportion reducing valve 42, hoisting crane.And open type controllable capacity pump 30, guide proportion reducing valve 42 and loading by pass valve 43 are connected with proportional reversing valve 41 respectively; Guide proportion reducing valve 42 flows to via proportional reversing valve 41 flow that loads by pass valve 43 for control presssure oil.Figure 4 illustrates proportional reversing valve 41 and take the situation of the proportional reversing valve of three, now B1 mouth can be blocked, as shown in Figure 4; Also can adopt the proportional reversing valve of two in addition.
Fig. 5 is the second basic structure schematic diagram according to the closed type hoisting negative power control system for crane of the embodiment of the present invention.As shown in Figure 5, the optional structure of the second of the open-circuit system 3 in closed type hoisting negative power control system for crane is to comprise: open type controllable capacity pump 30, is connected with auxiliary gear box 2, for obtaining power pressure oil output from auxiliary gear box 2; Solenoid directional control valve 51; Pilot operated directional control valve 52; Ratio loads by pass valve 53.Open type controllable capacity pump 30, solenoid directional control valve 51 and ratio load by pass valve 53 and are connected with pilot operated directional control valve 52 respectively; Solenoid directional control valve 51 is for controlling conducting or the shutoff of pilot operated directional control valve 52.In the structure shown in Fig. 5, solenoid directional control valve 51 can be controlled the switching of pilot operated directional control valve 52 mode of operations, to realize pressure oil and ratio, load by pass valve disconnection or be communicated with, the size of passing ratio loading by pass valve 53 controlled loading pressure realizes the step-less adjustment of on-load pressure.
Fig. 6 is the third basic structure schematic diagram according to the closed type hoisting negative power control system for crane of the embodiment of the present invention.As shown in Figure 6, the third optional structure of the open-circuit system 3 in closed type hoisting negative power control system for crane is to comprise: open type controllable capacity pump 30, is connected with auxiliary gear box 2, for obtaining power pressure oil output from auxiliary gear box 2; The first proportional reversing valve 621 and the second proportional reversing valve 622, be all connected with open type controllable capacity pump 30; First to fourth guide proportion reducing valve 611 to 614, wherein the first and second guide proportion reducing valves 611,612 are connected with the first proportional reversing valve 621, and the third and fourth guide proportion reducing valve is connected with the second proportional reversing valve 622; The amplitude oil cylinder 63 of hoisting crane and loading by pass valve 64, wherein the rodless cavity of amplitude oil cylinder 63 is connected with the second proportional reversing valve 622 with the first proportional reversing valve 621, the rod chamber of amplitude oil cylinder 63 is connected with the first proportional reversing valve 621, loads by pass valve 64 and is connected with the second proportional reversing valve 622.Amplitude oil cylinder 63 can absorb the power that open type controllable capacity pump 30 is obtained.The first guide proportion reducing valve 611 flows to the flow of the first hydraulic fluid port of amplitude oil cylinder 63 via the first proportional reversing valve 621 for control presssure oil; The second guide proportion reducing valve 612 flows to the flow of the second hydraulic fluid port of amplitude oil cylinder 63 via the first proportional reversing valve 621 for control presssure oil; The 3rd guide proportion reducing valve 613 flows to the flow of the first hydraulic fluid port of amplitude oil cylinder 63 via the second proportional reversing valve 622 for control presssure oil; The 4th guide proportion reducing valve 614 flows to via the second proportional reversing valve 622 flow that loads by pass valve 64 for control presssure oil.In Fig. 6, in the first hydraulic fluid port of amplitude oil cylinder 63, be rodless cavity, in the second hydraulic fluid port, be rod chamber.
Below the technical scheme of the present embodiment is described further.
Enclosed controllable capacity pump 31 forms closed system working connection with hoist motor 32, to hoisting speed reducer 33, provides kinetic energy with lifting heavy G, and in weight G decline process, its potential energy converting and energy is that kinetic energy passes to closed system.Driving engine is had an effect by auxiliary gear box and open-circuit system (by directly acting on open type controllable capacity pump) and closed system (by directly acting on enclosed controllable capacity pump) simultaneously.Auxiliary gear box is as an energy delivery mechanisms: it power of driving engine output can be passed to open type controllable capacity pump simultaneously and enclosed controllable capacity pump is realized externally acting, the negative power (under this operating mode, enclosed controllable capacity pump drives auxiliary gear box and turn of engine) producing when also weight in closed system can be declined passes to auxiliary gear box, by auxiliary gear box, passes to driving engine and open-circuit system.
The main operation element of closed system is enclosed controllable capacity pump and hoist motor.Enclosed controllable capacity pump is responsible for controlling the speed control that hoisting mechanism hoists and declines, and hoist motor is connected with reductor, is synchronized with rising and falling of weight.When weight hoists, driving engine is input to enclosed controllable capacity pump by auxiliary gear box by portion of energy, and now driving engine externally does work, and weight is raised.When weight declines, weight drives winch to rotate under Action of Gravity Field, thereby drives hoist motor and enclosed controllable capacity pump to rotate, and enclosed controllable capacity pump passes to auxiliary gear box by energy.This decline process is that enclosed controllable capacity pump is to auxiliary gear box and driving engine acting.Therefore for driving engine, this is a negative power (this operating mode of driving engine is external horsepower output, but absorbed power) and the energy that driving engine absorbs is limited.
The negative power P producing when weight declines
mfor:
P
m=M×g×V…………(1)
In formula (1): M represents lift heavy quality; G represents acceleration due to gravity; V represents weight descending speed.
The negative power that is delivered to closed system is P
cfor:
P
c=M×g×V×η
1×η
2…………(2)
In formula (2): η
1the mechanical efficiency that represents reductor and wire rope pulley group; η
2the mechanical efficiency that represents hydraulic efficiency pressure system.
The negative power P that driving engine absorbs
e=P
c, i.e. P
e=M * g * V * η
1* η
2(3)
P in formula
erepresent driving engine absorbed power.
From formula (3), can find out, the negative power that driving engine absorbs is directly proportional to the mass M of weight, and V is directly proportional to descending speed.And the absorbable negative power of driving engine is limited, therefore, when hoisting capacity M increases, the maximum falling speed V of weight should reduce.Along with the development of hoisting crane, the increase of hoisting capacity, only absorbs negative power by driving engine and can not satisfy the demands.
The launched machine of negative power and open-circuit system that weight decline produces absorb.The power that wherein driving engine absorbs is:
P
e=P
c-P
k…………(4)
In formula: P
krepresent the negative power that open-circuit system absorbs.
Draw thus the negative power that driving engine absorbs: P
e=MgV * η
1* η
2-P
k(5)
The negative power P that the present embodiment absorbs by controlling open-circuit system
k, realize the negative power P that driving engine absorbs
ebe less than its absorbable maximum negative power P
e≤ P
em(P wherein
emrepresent the absorbable maximum negative power of driving engine).
Take below the working process of the closed type hoisting negative power control system of Fig. 6 in example explanation the present embodiment.
In Fig. 6, the A2 mouth of the A1 mouth of the first proportional reversing valve 621 and the second proportional reversing valve 622 collaborates the rodless cavity fuel feeding to amplitude oil cylinder; The B1 mouth of the first proportional reversing valve 621 is amplitude oil cylinder 63 rod chamber fuel feeding; The B2 mouth of the second proportional reversing valve 622 is that ratio loads by pass valve 64 fuel feeding; The Median Function of the second proportional reversing valve 622 is " O " type function.Concrete control is as follows: when guide's proportional pressure-reducing valve 611,612,613 and 614 whole dead electricity, the first proportional reversing valve 621, the second proportional reversing valve 622 are in meta, and system is exported without pressure oil; When guide's proportional pressure-reducing valve 611 the first proportional reversing valve 621 is in the work of right position when electric, pressure oil enters amplitude oil cylinder 63 rodless cavities through the first proportional reversing valve 621 from A1 mouth, amplitude oil cylinder 63 realizes the action that hoists; When guide's proportional pressure-reducing valve 612 when electric, the first proportional reversing valve 621 is in the work of left position, pressure oil enters amplitude oil cylinder 63 rod chambers through the first proportional reversing valve from B1 mouth, luffing is realized down maneuver; When guide's proportional pressure-reducing valve 611,613 simultaneously when electric, pressure oil enters luffing rodless cavity through the first proportional reversing valve 621 from A1 mouth, pressure oil enters luffing rodless cavity through the second proportional reversing valve 622 from A2 mouth simultaneously, the high speed interflow while having realized amplitude-variation hoisting; When guide's proportional pressure-reducing valve 614 when electric, pressure oil enters ratio through the second proportional reversing valve 622 from B2 mouth and loads by pass valve 64.In figure, the control presssure of guide proportion reducing valve 611 to 614 outputs is proportional to control electric current, therefore can realize the ratio output of the first proportional reversing valve 621 and the second proportional reversing valve 622 flows, thereby realize the speed of amplitude oil cylinder or flow that ratio loads by pass valve is directly proportional to received current.
The negative power that open-circuit system absorbs is comprised of two parts, the power consuming when a part is moved for changing-breadth system, and a part is for loading the power consuming when by pass valve loads.Wherein the power of changing-breadth system consumption is that in hoisting process, operating mode determines (such as whether amplitude oil cylinder moves, the speed of action is that the requirement by actual condition determines), and the power of loading system to be us can control in real time, be a variable parameter.
P
K=Q
1×ΔP
1／600+Q
1×ΔP
2／600…………(6)
In formula: Q
1the flow that represents changing-breadth system; Δ P
1represent changing-breadth system pressure; Q
2represent to supply with loading by pass valve flow; Δ P
2represent to load by pass valve pressure;
Draw thus:
P
e=MgV×η
1×η
2-Q
1×ΔP
1／600-Q
2×ΔP
2／600…………(7)
The controller Real-Time Monitoring that the power stage state of driving engine itself can be carried by it draws, and passes to peripheral control system by CAN bus, and we are called engine loading rate.Engine loading rate=driving engine real output/engine rated power.In the situation that there is negative power, generally maintain engine loading rate in a fixed value (such as 5%), we regard it as target control value.
When load factor is during lower than expected value, increase the control electric current of guide proportion reducing valve 614, with scaling up change-over valve, export to the flow (Q in formula (7) that ratio loads by pass valve
2) make ratio load the increase of by pass valve consumed power, impel engine loading rate to return to expected value; Otherwise when engine loading rate is during higher than expected value, can reduce the electric current of guide proportion reducing valve 614, to reduce to load the consumption of power of by pass valve, make engine loading rate maintain expected value.
In addition, for system shown in Figure 5, when load factor is during lower than expected value, scaling up loads the received current of by pass valve 53, loads on-load pressure (the Δ P in formula (7) of by pass valve with scaling up
2) make ratio load the increase of by pass valve consumed power, impel engine loading rate to return to expected value; Otherwise when engine loading rate is during higher than expected value, can reduce the received current that ratio loads by pass valve 53, to reduce to load the consumption of power of by pass valve, make engine loading rate maintain expected value.
As the loading by pass valve employing electricity liquid ratio relief valve in the present embodiment, big or small (the Δ P in formula (7) of its pressure
2) can be by regulating its size of controlling electric current to realize stepless control.When load factor is lower, can make to control electric current relatively little, overshoot when by pass valve is opened reduces, and loads more steady.
By above system and control method, the negative power that is input to driving engine when enclosed elevator is transferred is no more than its absorbable maxim.No matter how hoisting capacity M and descending speed V change, all can be by electric guide proportion reducing valve 614 or ratio being loaded to the real-time control of by pass valve 53 size of current, and the driving engine making absorbs negative power and maintains goal-setting value.
As can be seen from the above description, the technical scheme of application the present embodiment, can obtain following beneficial effect:
The negative power producing when 1, enclosed elevator declines is delivered to open-circuit system by auxiliary gear box, by open-circuit system, is absorbed, and weight descending speed is no longer restricted;
2, by controlling the electric current of guide proportion reducing valve, realize proportional reversing valve and export to the flow proportional that ratio loads by pass valve and control, to obtain ratio, load the different loading power of by pass valve, owing to controlling as step-less adjustment, therefore load and stablize, can not make speed produce sudden change;
3, the pressure that ratio loads by pass valve also can step-less adjustment, and the negative power producing in closed system is little compared with low system overshoot compared with hour setting pressure, load more steady, when the negative power of closed system generation is larger, the higher satisfied loading power requirement of setting pressure;
4, no matter how the negative power of closed system output changes, all can by control the electric current of guide proportion reducing valve/or the electric current that ratio loads by pass valve make the power of driving engine maintain target control value;
5, the second proportional reversing valve 622 can be realized amplitude-variation hoisting and two functions of system loads, and more traditional mode has been saved a proportional reversing valve.
Obviously, those skilled in the art should be understood that, above-mentioned each module of the present invention or each step can realize with general computer device, they can concentrate on single computer device, or be distributed on the network that a plurality of computer devices form, alternatively, they can be realized with the executable program code of computer device, thereby, they can be stored in memory storage and be carried out by computer device, or they are made into respectively to each integrated circuit modules, or a plurality of modules in them or step are made into single integrated circuit module to be realized.Like this, the present invention is not restricted to any specific hardware and software combination.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection scope of the present invention.
Claims (10)
1. a closed type hoisting negative power control system for crane, the negative power producing when lift heavy thing is transferred for absorbing the hoisting mechanism of hoisting crane, is characterized in that, described control system comprises driving engine, auxiliary gear box, open-circuit system and closed system, wherein:
Described open-circuit system is connected with described auxiliary gear box respectively with closed system, and is connected to described driving engine by described auxiliary gear box;
Described closed system comprises the enclosed controllable capacity pump being connected with described auxiliary gear box, the hoist motor being connected with described enclosed controllable capacity pump by hydraulic tubing and the hoisting speed reducer being connected with described hoist motor;
Described auxiliary gear box for partly or entirely passing to described open-circuit system by described negative power when hoisting crane declines operation.
2. control system according to claim 1, is characterized in that, described open-circuit system comprises:
Open type controllable capacity pump, is connected with described auxiliary gear box, for obtaining power pressure oil output from described auxiliary gear box;
Proportional reversing valve, is connected with described open type controllable capacity pump;
The loading by pass valve of described hoisting crane, is connected with described proportional reversing valve;
Guide proportion reducing valve, is connected with described proportional reversing valve, for controlling described pressure oil, flows to the flow of described loading by pass valve via described proportional reversing valve.
3. control system according to claim 1, is characterized in that, described open-circuit system comprises:
Open type controllable capacity pump, is connected with described auxiliary gear box, for obtaining power pressure oil output from described auxiliary gear box;
Pilot operated directional control valve, is connected with described open type controllable capacity pump;
Ratio loads by pass valve, is connected with described pilot operated directional control valve;
Solenoid directional control valve, is connected with described pilot operated directional control valve, for controlling conducting or the shutoff of described pilot operated directional control valve.
4. control system according to claim 1, is characterized in that, described open-circuit system comprises:
Open type controllable capacity pump, is connected with described auxiliary gear box, for obtaining power pressure oil output from described auxiliary gear box;
The first and second proportional reversing valves, are all connected with described open type controllable capacity pump;
First to fourth guide proportion reducing valve, wherein the first and second guide proportion reducing valves are connected with the first proportional reversing valve, and the third and fourth guide proportion reducing valve is connected with the second proportional reversing valve;
Hydraulic Elements and loading by pass valve, the first hydraulic fluid port of wherein said Hydraulic Elements is connected with described the first and second proportional reversing valves, and the second hydraulic fluid port is connected with described the first proportional reversing valve, and described loading by pass valve is connected with described the second proportional reversing valve; And,
Described Hydraulic Elements are for absorbing the power that described open type controllable capacity pump is obtained;
Described the first guide proportion reducing valve flows to the flow of the first hydraulic fluid port of described Hydraulic Elements for controlling described pressure oil via described the first proportional reversing valve;
Described the second guide proportion reducing valve flows to the flow of the second hydraulic fluid port of described Hydraulic Elements for controlling described pressure oil via described the first proportional reversing valve;
Described the 3rd guide proportion reducing valve flows to the flow of the first hydraulic fluid port of described Hydraulic Elements for controlling described pressure oil via described the second proportional reversing valve;
Described the 4th guide proportion reducing valve flows to the flow of described loading by pass valve for controlling described pressure oil via described the second proportional reversing valve.
5. control system according to claim 4, is characterized in that, described loading by pass valve is that ratio loads by pass valve.
6. according to the control system described in claim 4 or 5, it is characterized in that, described Hydraulic Elements are that HM Hydraulic Motor or two plate valves that two plate valve interflow are controlled collaborate the telescopic oil cylinder of controlling.
7. according to the control system described in claim 4 or 5, it is characterized in that the amplitude oil cylinder that described Hydraulic Elements are described hoisting crane, the rodless cavity that described the first hydraulic fluid port is this amplitude oil cylinder, the rod chamber that described the second hydraulic fluid port is this amplitude oil cylinder.
8. control system according to claim 7, is characterized in that, described amplitude oil cylinder is two amplitude oil cylinder.
9. according to the control system described in claim 2,3 or 4, it is characterized in that, described open type controllable capacity pump is Load sensing pump or automatically controlled controllable capacity pump.
10. a hoisting crane, is characterized in that, comprises the closed type hoisting negative power control system for crane described in any one in claim 1 to 9.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110412215.0A CN102491173B (en) | 2011-12-12 | 2011-12-12 | Crane and closed type hoisting negative power control system for crane |
| PCT/CN2012/082075 WO2013086882A1 (en) | 2011-12-12 | 2012-09-26 | Crane, and closed-type hoist negative power control system for use with crane |
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|---|---|---|---|
| CN201110412215.0A CN102491173B (en) | 2011-12-12 | 2011-12-12 | Crane and closed type hoisting negative power control system for crane |
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| CN102491173B true CN102491173B (en) | 2014-04-02 |
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|---|---|---|---|---|
| CN102491173B (en) * | 2011-12-12 | 2014-04-02 | 中联重科股份有限公司 | Crane and closed type hoisting negative power control system for crane |
| CN103832314A (en) * | 2012-11-26 | 2014-06-04 | 徐州徐工随车起重机有限公司 | Road wrecker with U-type hanging arm |
| CN103350955B (en) * | 2013-07-25 | 2015-06-03 | 中联重科股份有限公司 | Crane, negative power system, negative power control method and negative power control equipment |
| CN108212335A (en) * | 2017-12-27 | 2018-06-29 | 徐工集团工程机械有限公司 | Crusher |
| CN110925252A (en) * | 2019-11-18 | 2020-03-27 | 中联重科股份有限公司 | Integrated multi-way valve, lifting hydraulic control system and crane |
| CN113582024B (en) * | 2021-06-17 | 2022-09-20 | 中联重科股份有限公司 | Negative power control method, equipment and system for crane and crane |
| CN113879995A (en) * | 2021-09-14 | 2022-01-04 | 徐州徐工基础工程机械有限公司 | Main winch variable load lowering control method and rotary drilling rig |
| CN113914173A (en) * | 2021-10-29 | 2022-01-11 | 柳工无锡路面机械有限公司 | Hydraulic control system of paver screed plate |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2013086882A1 (en) | 2013-06-20 |
| CN102491173A (en) | 2012-06-13 |
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