CN103244496A - Rotary control valve unit, rotary control hydraulic system and crane - Google Patents
Rotary control valve unit, rotary control hydraulic system and crane Download PDFInfo
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Abstract
The invention discloses a rotary control valve unit, a rotary control hydraulic system and a crane. The rotary control valve unit comprises a proportional reversing valve, a shuttle valve and a fixed-difference overflow valve, wherein two oil inlets of the shuttle valve are respectively communicated with two working oil ports of the proportional reversing valve, oil outlets of the shuttle valve are communicated with a second pressure sensing port of the fixed-difference overflow valve, a first pressure sensing port of the fixed-difference overflow valve is communicated with oil inlets of the proportional reversing valve, and overflow oil ports are communicated with an oil return path. Under the loading state, the two pressure sensing ports of the fixed-difference overflow valve sense the pressure of the oil inlets and the high-pressure working oil ports of the proportional reversing valve, when the difference of the two pressures is larger than a preset value, the overflow pressure of the fixed-difference overflow valve is correspondingly adjusted, part hydraulic oil of a high-pressure oil source enters the oil return path for decompression through the overflow oil ports of the fixed-difference overflow valve so as to stabilize the difference of oil pressure of the oil inlets and load pressure of the proportional reversing valve, accordingly the influence on flow of the high-pressure working oil ports caused by load pressure changing is reduced, and load flow stability is improved.
Description
Technical field
The present invention relates to hydraulics, particularly a kind of rotary control valve group, revolution control hydraulic system and hoist.
Background technique
Hoist is a kind of engineering machinery that can carry out operations such as material lifting, transportation and loading and unloading, extensively under operating modes such as building site, port and pier, oil field, railway, warehouse, wind-powered electricity generation, carried out hoisting operation and lifting operation, concrete as building bridge, install power generating equipment, shipbuilding, setting up wind power generating set etc.Hoist is saved manpower to reducing labor intensity, and reducings the construction costs, and improves construction weight, accelerates construction speed, and realizes that engineering construction mechanization plays a part very important.In recent years, along with the develop rapidly of national economy, the effect that hoist is brought into play in all conglomeraties is also increasing.Improvement to the hoist performance also more and more is subject to people's attention.
To have a volume little, in light weight in view of Hydraulic Power Transmission System, and compact structure is handled advantages such as light, and existing hoist adopts hydraulic transmission mostly.The hoist Hydraulic Power Transmission System comprises vehicle hydraulic system and following vehicle hydraulic system.Wherein, last vehicle hydraulic system mainly be divided into again hoist, stretch, luffing and revolution four parts.Above-mentioned Hydraulic slewing system be used for to realize the revolution operation of hoist, and the revolution operation makes hoist weight can be delivered to fast any spatial position in the assigned work scope, is the important component part that goes up vehicle hydraulic system.
The rotary control valve group is the core parts of Hydraulic slewing system, and it is used for control crane revolution action, and it is that collection speed governing, commutation, buffering, repairing are the valve group of one, and hoist fine motion (low-speed performance) is had material impact.The mode of speed regulation of crane rotation control valve group generally adopts metering pump to add proportional reversing valve by-pass throttle mode of speed regulation at present, proportional reversing valve plays the commutation speed governing, its filler opening and return opening communicate with high pressure fuel source and fuel tank respectively, and its first actuator port and second actuator port communicate with two actuator ports of rotary motor respectively.The defective of existing rotary control valve is: the non-constant valve port pressure reduction that causes of induced pressure is non-constant, cause the load flow instability, variation with load changes, to be the crane rotating speed with load variations change (can influence the size of revolution frictional force as the size in revolution gap, and then influence revolution fine motion, the weight of load also can influence revolution fine motion etc.), finally make the revolution fine motion instability of hoist.
Summary of the invention
In view of this, the present invention proposes a kind of rotary control valve group, utilizes this rotary control valve group can improve the stability of load flow.
The present invention also provides a kind of revolution control hydraulic system.Utilize this revolution control hydraulic system can improve the stability of hydraulic work system.
The present invention also provides hoist, to improve the revolution fretting performance of hoist.
The invention provides a kind of rotary control valve group, comprising: proportional reversing valve, described proportional reversing valve comprises: filler opening, return opening, first actuator port and second actuator port, filler opening communicates with high pressure fuel source, and return opening communicates with fuel tank; Described rotary control valve group also comprises shuttle valve and constant difference overflow valve; Wherein, two filler openings of shuttle valve communicate with two actuator ports of proportional reversing valve respectively, and oil outlet communicates with the second pressure sensitive mouth of constant difference overflow valve; The first pressure sensitive mouth of constant difference overflow valve communicates with the filler opening of proportional reversing valve, and the overflow hydraulic fluid port communicates with oil return circuit.
Further, above-mentioned rotary control valve group also comprises orifice valve, is arranged between constant difference overflow valve and the shuttle valve.
Further, described proportional reversing valve comprises filler opening, return opening, first actuator port and second actuator port, and filler opening communicates with high pressure fuel source, and return opening communicates with fuel tank; Described proportional reversing valve comprises three kinds of working staties: under first working state, filler opening communicates with first actuator port, and return opening communicates with second actuator port; Under second working state, filler opening, return opening, first actuator port and second actuator port all end, or filler opening communicates with return opening, and first actuator port and second actuator port end; Under the 3rd working state, filler opening communicates with second actuator port, and return opening communicates with first actuator port.
Further, described proportional reversing valve is the hydraulic control proportional reversing valve.
Further, above-mentioned rotary control valve group also comprises: first relief valve, and its filler opening communicates with first actuator port, and the overflow hydraulic fluid port communicates with second actuator port; Second relief valve, its filler opening communicates with second actuator port, and the overflow hydraulic fluid port communicates with first actuator port.
Further, above-mentioned rotary control valve group also comprises: first one-way valve, and its oil outlet communicates with first actuator port, and filler opening communicates with return opening; Second one-way valve, its oil outlet communicates with second actuator port, and filler opening communicates with return opening.
Further, above-mentioned rotary control valve group also comprises: back pressure valve, the oil outlet of the oil outlet of first one-way valve and second one-way valve communicates with oil return circuit by described back pressure valve.
The invention provides a kind of revolution control hydraulic system, comprise: oil hydraulic pump, executive component and above-mentioned any described rotary control valve group, the filler opening of the proportional reversing valve of rotary control valve group communicates with the oil drain out of oil hydraulic pump, and first actuator port and second actuator port communicate with two actuator ports of described executive component respectively.
Further, described oil hydraulic pump is metering pump, and/or described executive component is rotary motor.
The invention provides a kind of hoist, be provided with above-mentioned arbitrary revolution control hydraulic system.
The invention provides a kind of rotary control valve, with respect to existing rotary control valve group, rotary control valve group provided by the invention is provided with shuttle valve and constant difference overflow valve, two actuator ports that two filler openings of shuttle valve are arranged at proportional reversing valve communicate, and two pressure sensitive mouths of constant difference overflow valve communicate with the oil outlet of shuttle valve and the filler opening of proportional reversing valve respectively.Under load condition, shuttle valve can feed back to induced pressure the second pressure sensitive mouth of constant difference overflow valve, the filler opening of high pressure fuel source passing ratio selector valve communicates with the first pressure sensitive mouth of constant difference overflow valve, when the difference of the filler opening pressure of proportional reversing valve and high-pressure work hydraulic fluid port pressure during greater than predetermined value, the corresponding adjustment of constant difference overflow valve oil pressure relief, and then the overflow hydraulic fluid port of the part hydraulic oil of high pressure fuel source by constant difference overflow valve enters oil return circuit and carries out pressure release, poor with the oil pressure of stablizing the proportional reversing valve filler opening and induced pressure, reduce load thus to the influence of high-pressure work hydraulic fluid port flow, improve the stability of load flow.
The present invention also provides a kind of rotary control system that is provided with above-mentioned rotary control valve, and above-mentioned rotary control valve has the stable characteristics of load flow, has improved the stability of this flow rate of hydraulic system and work thus.
The present invention also provides a kind of hoist that is provided with above-mentioned rotary control system, because this hydraulic system load flow is stable, the stability of crane rotating speed is improved, and then improves the fretting performance of crane rotation.Those skilled in the art can come the control load flow by the valve port area that disposes logical proportional reversing valve, so that the revolution fine motion of hoist reaches optimum efficiency.
Description of drawings
The accompanying drawing that constitutes a part of the present invention is used to provide further understanding of the present invention, and illustrative examples of the present invention and explanation thereof are used for explaining the present invention, do not constitute improper restriction of the present invention.In the accompanying drawings:
The principle schematic of the rotary control valve group that Fig. 1 provides for the embodiment of the invention one;
The principle schematic of hydraulic system is controlled in the revolution that Fig. 2 provides for the embodiment of the invention two.
Description of reference numerals:
1 back pressure valve, 2 proportional reversing valves
31 first one-way valves, 32 second one-way valves
41 first relief valves, 42 second relief valves
5 shuttle valves, 6 orifice valves
7 constant difference overflow valves, 10 rotary control valve groups
11 oil hydraulic pumps, 12 executive components
P filler opening T return opening
The A first actuator port B second actuator port
The second pressure sensitive mouth of the first pressure sensitive mouth a2 constant difference overflow valve of a1 constant difference overflow valve
The overflow hydraulic fluid port K break oil-feed port of b constant difference overflow valve
Embodiment
Need to prove that under the situation of not conflicting, embodiment and the feature among the embodiment among the present invention can make up mutually.Below in conjunction with accompanying drawing, each preferred embodiment of the present invention is described further.
In the presents, unless otherwise specified, the nouns of locality such as described left side position, right position, upper, the next and meta all are that the basis is determined with the respective drawings.Below be that example is described embodiment provided by the invention with the hydraulic system that is applied to hoist.
Please refer to Fig. 1, this figure is the principle schematic of the rotary control valve group that provides of the embodiment of the invention one.This rotary control valve group comprises proportional reversing valve 2, shuttle valve 5 and constant difference overflow valve 7.Wherein:
Two filler openings of shuttle valve 5 communicate with two actuator ports of proportional reversing valve 2 respectively, and oil outlet communicates with the second pressure sensitive mouth a2 of constant difference overflow valve 7, and concrete, the second pressure sensitive mouth a2 communicates with the spring chamber of constant difference overflow valve 7.The effect of shuttle valve 5 is induced pressure (being the pressure of high-pressure work hydraulic fluid port) is fed back to the spring chamber of constant difference overflow valve 7.
The first pressure sensitive mouth a1 of constant difference overflow valve 7 communicates with the oil inlet P of proportional reversing valve 2, and overflow hydraulic fluid port b communicates with oil return circuit.The effect of constant difference overflow valve 7 is the oil inlet P oil pressure of stabilization ratio example selector valve 2 and the pressure reduction of induced pressure, reduce load to the influence of high-pressure work hydraulic fluid port pressure, those skilled in the art can come the regulating load flow by the area of regulating proportional reversing valve 2 oil inlet P.
The annexation of above-mentioned hydraulic element is:
The oil inlet P of proportional reversing valve 2 communicates with high pressure fuel source, and oil return inlet T communicates with fuel tank, and the first actuator port A and the second actuator port B communicate with two actuator ports of rotary motor respectively.The oil inlet P of aforementioned proportion selector valve 2, oil return inlet T, the first actuator port A and the second actuator port B form filler opening, return opening, first actuator port and second actuator port of rotary control valve group respectively.
The working principle of above-mentioned rotary control valve group is:
At holding state, proportional reversing valve 2 is in meta, and the hydraulic oil that high pressure fuel source provides is directly by constant difference overflow valve 7 low pressure off-loads.Certainly, aforementioned proportion selector valve 2 all right following settings: when being in meta, oil inlet P communicates with oil return inlet T, and hydraulic oil is directly by the oil return inlet T draining thus.
Load condition, the state when namely utilizing above-mentioned rotary control valve group to turn round operation:
With the first actuator port A oil-feed, the second actuator port B oil return is for clockwise rotating, the second actuator port B oil-feed, and the first actuator port A oil return is example for rotating counterclockwise: when turning round along clockwise direction, proportional reversing valve 2 is in position, a left side.At this moment, in proportional reversing valve 2, oil inlet P and its first actuator port A communicate, oil return inlet T and its second actuator port B communicate, the pressure of the first actuator port A is greater than the second actuator port B, it is induced pressure, this moment, the oil outlet of shuttle valve 5 communicated with the first actuator port A, the part hydraulic oil of A mouth flows into the second pressure sensitive mouth a2 of constant difference overflow valve 7, high pressure fuel source enters the first pressure sensitive mouth a1 of constant difference overflow valve 7, the overflow hydraulic fluid port b of part high pressure oil by constant difference overflow valve 7 enters the oil return circuit pressure release, is definite value with the high pressure oil pressure (being the pressure of proportional reversing valve 2 oil inlet P) of stablize remainder and the difference of induced pressure.The high pressure oil of remainder is the oil inlet P, first actuator port that the first actuator port A enters rotary motor of passing ratio selector valve 2 successively, the second actuator port B, the oil return inlet T of passing ratio selector valve 2 flow back to fuel tank to the hydraulic oil that second actuator port of rotary motor is discharged successively, the circulation of realization hydraulic pressure, rotary motor can change oil pressure into the mechanical energy conversion, is used for realizing the steadily rotation motion clockwise of crane.
When turning round in the counterclockwise direction, proportional reversing valve 2 is in right position.At this moment, in proportional reversing valve 2, oil inlet P and its second actuator port B communicate, oil return inlet T and its first actuator port A communicate, the pressure of the first actuator port A is less than the second actuator port B, the second actuator port B is induced pressure, this moment, the oil outlet of shuttle valve 5 communicated with the second actuator port B, the part hydraulic oil of B mouth flows into the second pressure sensitive mouth a2 of constant difference overflow valve 7, high pressure fuel source enters the first pressure sensitive mouth a1 of constant difference overflow valve 7, and the overflow hydraulic fluid port b of a high pressure oil part by constant difference overflow valve 7 enters oil return circuit, and to carry out pressure release be definite value with the high pressure oil pressure of stablizing remainder and the difference of induced pressure.The high pressure oil of remainder flows to turn state is opposite clockwise, the steadily rotation motion counterclockwise of crane.
Thus, under load condition, shuttle valve 5 feeds back to induced pressure the second pressure sensitive mouth a2 of constant difference overflow valve 7, high pressure fuel source communicates with the second pressure sensitive mouth a2 of constant difference overflow valve 7, when the difference of the pressure of high pressure fuel source and induced pressure during greater than predetermined value, the overflow hydraulic fluid port b of the part hydraulic oil of high pressure fuel source by constant difference overflow valve 7 enters oil return circuit and carries out pressure release, poor with the oil pressure of stablizing proportional reversing valve 2 oil inlet P and induced pressure, reduce the influence that induced pressure is changed to load flow, and then the stability of raising load flow, be that the crane rotating speed is stable, improve the fretting performance of hoist.Those skilled in the art can come the control load flow by the valve port area that disposes logical proportional reversing valve 2, so that the revolution fine motion of hoist reaches optimum efficiency.
Refer again to Fig. 1, among the embodiment one, the rotary control valve group also comprises orifice valve 6, and this orifice valve 6 is arranged between constant difference overflow valve 7 and the shuttle valve 5.Wherein, the filler opening of orifice valve 6 communicates with the oil outlet of shuttle valve 5, and the oil outlet of orifice valve 6 communicates with the second pressure sensitive mouth a2 of constant difference overflow valve 7.The pressure of the hydraulic oil that the oil outlet of shuttle valve 5 is discharged is identical with induced pressure, because induced pressure usually has fluctuation, the effect that this orifice valve 6 can play filtering voltage regulation is set, and the pressure of the high-pressure work hydraulic fluid port by stablizing shuttle valve 5 feedback comes further steady load flow.
In addition, in order to improve the revolution shock-absorbing capacity of this rotary control valve group, the rotary control valve group that embodiment one provides can also comprise: first relief valve 41, and its filler opening communicates with the first actuator port A, and the overflow hydraulic fluid port communicates with the second actuator port B; Second relief valve 42, its filler opening communicates with the second actuator port B, and the overflow hydraulic fluid port communicates with the first actuator port A.
Like this, when the pressure of the first actuator port A reaches predetermined value, the filler opening of first relief valve 41 and overflow hydraulic fluid port conducting off-load; Similarly, when the pressure of the second actuator port B reaches predetermined value, the filler opening of second relief valve 42 and overflow hydraulic fluid port conducting off-load.When rotary motor revolution or revolution stop, if the pressure of arbitrary actuator port rises to predetermined value, relief valve conducting off-load is arranged all, and then realize buffer function improving the stability of rotary motor work thus, prolong the working life of hydraulic element.
Further, in order to improve the negative moment repairing performance of rotary control valve group, the rotary control valve group that embodiment one provides can also comprise: first one-way valve 31, and its oil outlet communicates with the first actuator port A, and filler opening communicates with oil return inlet T; Second one-way valve 32, its oil outlet communicates with the second actuator port B, and filler opening communicates with oil return inlet T.Thus, form the repairing oil circuit between the filler opening of first one-way valve 31 and the oil return inlet T and between the oil outlet of second one-way valve 32 and the oil return inlet T.
If the sense of rotation of the direction of moment of face and rotary motor is identical, as heavy duty, revolution when at a high speed slide car phenomenon occurring to idling or revolution, rotary motor will speed up revolution, the oil pump feed deficiency, cause a side negative pressure, when the first actuator port A place produced negative pressure, the hydraulic oil in the repairing oil circuit was the first actuator port A repairing by first one-way valve 31; Similarly, when the second actuator port B place produced negative pressure, the hydraulic oil in the repairing oil circuit was the second actuator port B repairing by second one-way valve 32.Thus, return pressure will be opened above-mentioned one-way valve and carry out repairing, prevent rotary motor idle running, play the effect of protection rotary motor.
In addition, in order to improve return oil pressure, make repairing more abundant, above-mentioned rotary control valve group also comprises preferably the oil outlet of back pressure valve 1, the first one-way valve 31 and the oil outlet of second one-way valve 32 communicates with oil return circuit by this back pressure valve 1.
Above-mentioned rotary control valve group also preferably is provided with break oil-feed port K, and this break oil-feed port K communicates with oil inlet P, and a part of high pressure fuel source is the break fuel feeding by this hydraulic fluid port thus, realizes the startup of break.
As shown in the above, with respect to existing rotary control valve group, the rotary control valve group that the embodiment of the invention provides is provided with shuttle valve and constant difference overflow valve.Under load condition, shuttle valve can feed back to induced pressure the second pressure sensitive mouth of constant difference overflow valve, high pressure fuel source communicates with the second pressure sensitive mouth of constant difference overflow valve, when the difference of the pressure of the pressure of proportional reversing valve filler opening and induced pressure during greater than predetermined value, the corresponding adjustment of constant difference overflow valve oil pressure relief, and then the overflow hydraulic fluid port of the part hydraulic oil of high pressure fuel source by constant difference overflow valve enters oil return circuit and carries out pressure release, poor with the oil pressure of stablizing the proportional reversing valve filler opening and induced pressure, reduce load thus to the influence of load flow, improve the stability of load flow.
See also Fig. 2, this figure is the principle schematic of the revolution control hydraulic system that provides of the embodiment of the invention two.This revolution control hydraulic system comprises: oil hydraulic pump 11, executive component 12 and above-mentioned rotary control valve group 10, the oil inlet P of the proportional reversing valve 2 of rotary control valve group 10 communicates with the oil drain out of oil hydraulic pump 11, and the first actuator port A and the second actuator port B communicate with two actuator ports of executive component respectively.For the above-mentioned revolution control hydraulic system that is applied to hoist, oil hydraulic pump 11 can be metering pump, and executive component 12 can be rotary motor.
Because the revolution that present embodiment provides control hydraulic system is provided with above-mentioned rotary control valve group, therefore this revolution control hydraulic system also has the stable advantage of load flow, and the crane rotating speed is stable, is conducive to improve the fretting performance of crane rotation.Be appreciated that above-mentioned revolution control hydraulic system also can be applied in the Other Engineering equipment, to carry out revolute function.
The embodiment of the invention three also provides a kind of hoist, and above-mentioned revolution control hydraulic system is set.Hydraulic actuator is rotary motor, and the output shaft of rotary motor links to each other with speed reducer, and this speed reducer and pivoting support gear are connected.Because above-mentioned this revolution control hydraulic system has the stable advantage of load flow, the hoist that therefore is provided with this revolution control hydraulic system also possesses corresponding technique effect, and its specific implementation process is similar to the above embodiments, does not give unnecessary details now.
The above only is preferred embodiment of the present invention, and is in order to limit the present invention, within the spirit and principles in the present invention not all, any modification of doing, is equal to replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. rotary control valve group, comprise proportional reversing valve (2), described proportional reversing valve comprises: filler opening (P), return opening (T), first actuator port (A) and second actuator port (B), and filler opening (P) communicates with high pressure fuel source, and return opening (T) communicates with fuel tank; It is characterized in that described rotary control valve group also comprises shuttle valve (5) and constant difference overflow valve (7); Wherein,
Two filler openings of shuttle valve (5) communicate with two actuator ports of proportional reversing valve (2) respectively, and oil outlet communicates with the second pressure sensitive mouth (a2) of constant difference overflow valve (7);
The first pressure sensitive mouth (a1) of constant difference overflow valve (7) communicates with the filler opening (P) of proportional reversing valve (2), and overflow hydraulic fluid port (b) communicates with oil return circuit.
2. rotary control valve group according to claim 1 is characterized in that, also comprises orifice valve (6), is arranged between constant difference overflow valve (7) and the shuttle valve (5).
3. rotary control valve group according to claim 2 is characterized in that, described proportional reversing valve (2) comprises three kinds of working staties:
Under first working state, filler opening (P) communicates with first actuator port (A), and return opening (T) communicates with second actuator port (B);
Under second working state, filler opening (P), return opening (T), first actuator port (A) and second actuator port (B) all end, or filler opening (P) communicates with return opening (T), and first actuator port (A) and second actuator port (B) end;
Under the 3rd working state, filler opening (P) communicates with second actuator port (B), and return opening (T) communicates with first actuator port (A).
4. rotary control valve group according to claim 3 is characterized in that, described proportional reversing valve (2) is the hydraulic control proportional reversing valve.
5. rotary control valve group according to claim 3 is characterized in that, also comprises:
First relief valve (41), its filler opening communicates with first actuator port (A), and the overflow hydraulic fluid port communicates with second actuator port (B);
Second relief valve (42), its filler opening communicates with second actuator port (B), and the overflow hydraulic fluid port communicates with first actuator port (A).
6. rotary control valve group according to claim 5 is characterized in that, also comprises:
First one-way valve (31), its oil outlet communicates with first actuator port (A), and filler opening communicates with return opening (T);
Second one-way valve (32), its oil outlet communicates with second actuator port (B), and filler opening communicates with return opening (T).
7. rotary control valve group according to claim 6 is characterized in that, also comprises: back pressure valve (1), the oil outlet of the oil outlet of first one-way valve (31) and second one-way valve (32) communicates with oil return circuit by described back pressure valve (1).
8. hydraulic system is controlled in a revolution, it is characterized in that, comprise: any described rotary control valve group of oil hydraulic pump, executive component and claim 1 to 7, the filler opening (P) of the proportional reversing valve of rotary control valve group (2) communicates with the oil drain out of oil hydraulic pump, and first actuator port (A) and second actuator port (B) communicate with two actuator ports of described executive component respectively.
9. revolution control hydraulic system according to claim 8 it is characterized in that described oil hydraulic pump is metering pump, and/or described executive component is rotary motor.
10. a hoist is characterized in that, is provided with claim described 8 or 9 described revolution control hydraulic systems.
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