CN103244496B - Rotary control valve group, revolution hydraulic control system and hoist - Google Patents
Rotary control valve group, revolution hydraulic control system and hoist Download PDFInfo
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Abstract
The invention discloses a kind of rotary control valve group, revolution hydraulic control system and hoist.Above-mentioned rotary control valve group comprises proportional reversing valve, shuttle valve and constant difference overflow valve; 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; First pressure sensitive mouth of constant difference overflow valve communicates with the filler opening of proportional reversing valve, and overflow hydraulic fluid port communicates with oil return circuit.Under load condition, the pressure of constant difference overflow valve two pressure sensitive proportional reversing valve filler openings and high-pressure work hydraulic fluid port, when the difference of the two pressure is greater than predetermined value, the corresponding adjustment of constant difference overflow valve oil pressure relief, the section hydraulic oil of high pressure fuel source enters oil return circuit by the overflow hydraulic fluid port of constant difference overflow valve and carries out pressure release, with the stable oil pressure of proportional reversing valve filler opening and the difference of induced pressure, reduce the impact of induced pressure change on high-pressure work hydraulic fluid port flow thus, improve the stability of load flow.
Description
Technical field
The present invention relates to hydraulics, particularly a kind of rotary control valve group, revolution hydraulic control system and hoist.
Background technique
Hoist is a kind of engineering machinery can carrying out the operations such as material lifting, transport and handling, extensively under the 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 built bridge, installing power generating equipment, shipbuilding, erection wind power generating set etc.Hoist, to reducing labor intensity, is saved manpower, is reducingd the construction costs, and improves construction weight, Accelerating The Construction speed, and realizes engineering construction mechanization and play a very important role.In recent years, along with the develop rapidly of national economy, the effect that hoist plays in all conglomeraties is also increasing.The improvement of hoist performance is also more and more subject to people's attention.
In view of Hydraulic Power Transmission System, to have volume little, lightweight, and compact structure, handles the advantages such as light, and existing hoist adopts hydraulic transmission mostly.Hoist Hydraulic Power Transmission System comprises vehicle hydraulic system and lower vehicle hydraulic system.Wherein, upper vehicle hydraulic system be mainly divided into again hoist, stretch, luffing and revolution four part.Above-mentioned Hydraulic slewing system is for realizing the revolution operation of hoist, and revolution operation enables hoist weight be delivered to fast any spatial position within the scope of assigned work, is the important component part of upper vehicle hydraulic system.
Rotary control valve group is the core parts of Hydraulic slewing system, and it is for controlling crane revolution action, and it is the valve group integrating speed governing, commutation, buffering, repairing, has material impact to hoist fine motion (low-speed performance).The mode of speed regulation of current crane rotation control valve group generally adopts metering pump to add proportional reversing valve by-pass throttle mode of speed regulation, proportional reversing valve works the speed governing that commutates, its filler opening and return opening communicate with high pressure fuel source and fuel tank respectively, and its first actuator port and the second actuator port communicate with two actuator ports of rotary motor respectively.The defect of existing rotary control valve is: the non-constant valve port pressure reduction that causes of induced pressure is non-constant, cause load flow unstable, change with the change of load, namely crane rotating speed changes with load variations (can affect the size of revolution frictional force as turned round the size in gap, and then impact revolution fine motion, the weight of load also can affect revolution fine motion etc.), finally make the revolution fine motion of hoist unstable.
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 hydraulic control system.Utilize this revolution hydraulic control 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, the first actuator port and the second actuator port, and 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; First pressure sensitive mouth of constant difference overflow valve communicates with the filler opening of proportional reversing valve, and 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 shuttle valve.
Further, described proportional reversing valve comprises filler opening, return opening, the first actuator port and the 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: in the first operative state, and filler opening communicates with the first actuator port, and return opening communicates with the second actuator port; In a second operative state, filler opening, return opening, the first actuator port and the second actuator port all end, or filler opening communicates with return opening, the first actuator port and the cut-off of the second actuator port; Under the 3rd working state, filler opening communicates with the second actuator port, and return opening communicates with the first actuator port.
Further, described proportional reversing valve is hydraulic control proportional reversing valve.
Further, above-mentioned rotary control valve group also comprises: the first relief valve, and its filler opening communicates with the first actuator port, and overflow hydraulic fluid port communicates with the second actuator port; Second relief valve, its filler opening communicates with the second actuator port, and overflow hydraulic fluid port communicates with the first actuator port.
Further, above-mentioned rotary control valve group also comprises: the first one-way valve, and its oil outlet communicates with the first actuator port, and filler opening communicates with return opening; Second one-way valve, its oil outlet communicates with the second actuator port, and filler opening communicates with return opening.
Further, above-mentioned rotary control valve group also comprises: back pressure valve, and the oil outlet of the first one-way valve and the oil outlet of the second one-way valve are communicated with oil return circuit by described back pressure valve.
The invention provides a kind of revolution hydraulic control system, comprise: oil hydraulic pump, executive component and the rotary control valve group described in above-mentioned any one, the filler opening of the proportional reversing valve of rotary control valve group communicates with the oil drain out of oil hydraulic pump, and the first actuator port and the 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 hydraulic control system.
The invention provides a kind of rotary control valve, relative 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.In the loaded state, shuttle valve can by load pressure feedback to 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 inlet pressure of proportional reversing valve and the difference of high-pressure work hydraulic fluid port pressure are greater than predetermined value, the corresponding adjustment of constant difference overflow valve oil pressure relief, and then the section hydraulic oil of high pressure fuel source enters oil return circuit by the overflow hydraulic fluid port of constant difference overflow valve and carries out pressure release, with the stable oil pressure of proportional reversing valve filler opening and the difference of induced pressure, reduce load thus to the impact 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 being provided with above-mentioned rotary control valve, and above-mentioned rotary control valve has the stable feature of load flow, which thereby enhances the stability of this flow rate of hydraulic system and work.
The present invention also provides a kind of hoist being provided with above-mentioned rotary control system, and because this hydraulic system load flow is stablized, the stability of crane rotating speed is improved, and then improves the fretting performance of crane rotation.Those skilled in the art carry out control load flow by the valve port area configuring logical proportional reversing valve, reach optimum efficiency to make the revolution fine motion of hoist.
Accompanying drawing explanation
The accompanying drawing forming a part of the present invention is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation 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 present invention one;
The principle schematic of the revolution hydraulic control system that Fig. 2 provides for the embodiment of the present invention two.
Description of reference numerals:
1 back pressure valve 2 proportional reversing valve
31 first one-way valve 32 second one-way valves
41 first relief valve 42 second relief valves
5 shuttle valve 6 orifice valves
7 constant difference overflow valve 10 rotary control valve groups
11 oil hydraulic pump 12 executive components
P filler opening T return opening
A first actuator port B second actuator port
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
It should be noted that, when not conflicting, the embodiment in the present invention and the feature in embodiment can combine mutually.Below in conjunction with accompanying drawing, each preferred embodiment of the present invention is described further.
In presents, unless otherwise specified, the noun of locality such as described left position, right position, upper, the next and meta is all determined based on respective drawings.For the hydraulic system being applied to hoist, embodiment provided by the invention is described below.
Please refer to Fig. 1, this figure is the principle schematic of the rotary control valve group that the embodiment of the present invention one provides.This rotary control valve group comprises proportional reversing valve 2, shuttle valve 5 and constant difference overflow valve 7.Wherein:
Proportional reversing valve 2 can be existing selector valve, and for the running by the hydraulic control oil flow direction and flow control executive component, executive component is rotary motor, hydraulic energy can be converted to mechanical energy and drive crane revolution.This selector valve can be pilot operated directional control valve, solenoid directional control valve or hand control change-over valve, preferably pilot operated directional control valve is adopted in the present embodiment, concrete, in this example, proportional reversing valve 2 is hydraulic control three position four-way directional control valve, has oil inlet P, oil return inlet T, the first actuator port A, the second actuator port B.This proportional reversing valve 2 has three positions: during meta, each hydraulic fluid port remain off; During left position, oil inlet P communicates with the first actuator port A, and oil return inlet T communicates with the second actuator port B; During right position, oil inlet P communicates with the second actuator port B, and oil return inlet T communicates with the first actuator port A.
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, concrete, and the second pressure sensitive mouth a2 communicates with the spring chamber of constant difference overflow valve 7.The effect of shuttle valve 5 is spring chamber induced pressure (i.e. the pressure of high-pressure work hydraulic fluid port) being fed back to constant difference overflow valve 7.
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 stabilization ratio example oil inlet P oil pressure of selector valve 2 and the pressure reduction of induced pressure, reduce load to the impact of high-pressure work hydraulic fluid port pressure, those skilled in the art carry out regulating load flow by regulating the area of 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 communicates 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 the filler opening of rotary control valve group, return opening, the first actuator port and the second actuator port 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 load discharge.Certainly, aforementioned proportion selector valve 2 can also be arranged as follows: when being in meta, oil inlet P communicates with oil return inlet T, and hydraulic oil is directly by oil return inlet T draining thus.
Load condition, namely utilize above-mentioned rotary control valve group carry out turn round operation time state:
With the first actuator port A oil-feed, the second actuator port B oil return is for rotating clockwise, and the second actuator port B oil-feed, the first actuator port A oil return is for rotating counterclockwise as example: when turning round along clockwise direction, proportional reversing valve 2 is in left position.Now, 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, now the oil outlet of shuttle valve 5 communicates with the first actuator port A, the section 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, part high pressure oil enters oil return circuit pressure release by the overflow hydraulic fluid port b of constant difference overflow valve 7, with the difference of the high pressure oil pressure of stable remainder (i.e. the pressure of proportional reversing valve 2 oil inlet P) and induced pressure for definite value.The high pressure oil of the remainder successively oil inlet P of passing ratio selector valve 2, the first actuator port A enters the first actuator port of rotary motor, second actuator port B of passing ratio selector valve 2, oil return inlet T flow back to fuel tank to second actuator port of the rotary motor hydraulic oil of discharging successively, realize hydraulic circulation, oil pressure can be changed into mechanical energy conversion by rotary motor, for realizing the steadily rotation motion clockwise of crane.
When turning round in the counterclockwise direction, proportional reversing valve 2 is in right position.Now, 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, second actuator port B is induced pressure, now the oil outlet of shuttle valve 5 communicates with the second actuator port B, the section 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, a high pressure oil part enters oil return circuit by the overflow hydraulic fluid port b of constant difference overflow valve 7 and carries out pressure release with the difference of the high pressure oil pressure of stable remainder and induced pressure for definite value.The high-pressure oil flow of remainder to contrary with clockwise turn state, the counterclockwise steadily rotation motion of crane.
Thus, in the loaded state, shuttle valve 5 by load pressure feedback to 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 is greater than predetermined value, the section hydraulic oil of high pressure fuel source enters oil return circuit by the overflow hydraulic fluid port b of constant difference overflow valve 7 and carries out pressure release, with the stable oil pressure of proportional reversing valve 2 oil inlet P and the difference of induced pressure, reduce the impact that induced pressure is changed to load flow, and then improve the stability of load flow, namely crane rotating speed is stablized, improve the fretting performance of hoist.Those skilled in the art carry out control load flow by the valve port area configuring logical proportional reversing valve 2, reach optimum efficiency to make the revolution fine motion of hoist.
Refer again to Fig. 1, in embodiment one, rotary control valve group also comprises orifice valve 6, and this orifice valve 6 is arranged between constant difference overflow valve 7 and 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 of the oil outlet discharge of shuttle valve 5 is identical with induced pressure, because induced pressure usually has fluctuation, arrange the effect that this orifice valve 6 can play filtering voltage regulation, the pressure of the high-pressure work hydraulic fluid port fed back by stable shuttle valve 5 carrys out 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: the first relief valve 41, and its filler opening communicates with the first actuator port A, and 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 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 the first relief valve 41 and overflow hydraulic fluid port conducting off-load; Similar, when the pressure of the second actuator port B reaches predetermined value, the filler opening of the second relief valve 42 and overflow hydraulic fluid port conducting off-load.Thus when rotary motor revolution or revolution stop, if the pressure increase of any operative hydraulic fluid port is to predetermined value, all there is relief valve conducting off-load, and then realize buffer function, improve the stability of rotary motor work, extend 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: the 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, repairing oil circuit is formed between the filler opening of the first one-way valve 31 and oil return inlet T and between the oil outlet of the second one-way valve 32 and oil return inlet T.
If the direction of moment of face is identical with the sense of rotation of rotary motor, as heavy duty, turn round by when occurring slipping car phenomenon to idling or revolution at a high speed, rotary motor will speed up revolution, oil pump feed is not enough, cause side negative pressure, when the first actuator port A place produces negative pressure, the hydraulic oil in repairing oil circuit is the first actuator port A repairing by the first one-way valve 31; Similar, when the second actuator port B place produces negative pressure, the hydraulic oil in repairing oil circuit is the second actuator port B repairing by the second one-way valve 32.Thus, return pressure will be opened above-mentioned one-way valve and carry out repairing, prevent rotary motor from dallying, and 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 back pressure valve 1, and the oil outlet of the first one-way valve 31 and the oil outlet of the second one-way valve 32 are communicated with oil return circuit by this back pressure valve 1.
Above-mentioned rotary control valve group is also preferably 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 break fuel feeding by this hydraulic fluid port thus, realizes the startup of break.
As shown in the above, relative to existing rotary control valve group, the rotary control valve group that the embodiment of the present invention provides is provided with shuttle valve and constant difference overflow valve.In the loaded state, shuttle valve can by load pressure feedback to 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 proportional reversing valve filler opening and the pressure of induced pressure is greater than predetermined value, the corresponding adjustment of constant difference overflow valve oil pressure relief, and then the section hydraulic oil of high pressure fuel source enters oil return circuit by the overflow hydraulic fluid port of constant difference overflow valve and carries out pressure release, with the stable oil pressure of proportional reversing valve filler opening and the difference of induced pressure, reduce load thus to the impact of load flow, improve the stability of load flow.
Refer to Fig. 2, this figure is the principle schematic of the revolution hydraulic control system that the embodiment of the present invention two provides.This revolution hydraulic control 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 communicates with two actuator ports of executive component respectively.For the above-mentioned revolution hydraulic control system being applied to hoist, oil hydraulic pump 11 can be metering pump, and executive component 12 can be rotary motor.
The revolution hydraulic control Operation system setting provided due to the present embodiment has above-mentioned rotary control valve group, and therefore this revolution hydraulic control system also has the stable advantage of load flow, and crane rotating speed is stablized, and is conducive to the fretting performance improving crane rotation.Be appreciated that above-mentioned revolution hydraulic control system also can be applied in Other Engineering equipment, to perform revolute function.
The embodiment of the present invention three also provides a kind of hoist, arranges above-mentioned revolution hydraulic control system.Hydraulic actuator is rotary motor, and the output shaft of rotary motor is connected with speed reducer, and this speed reducer and pivoting support gear are connected.Because this revolution hydraulic control system above-mentioned has the stable advantage of load flow, the hoist being therefore provided with this revolution hydraulic control system also possesses corresponding technique effect, and its specific implementation process is similar to the above embodiments, does not hereby repeat.
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. a rotary control valve group, comprise proportional reversing valve (2), described proportional reversing valve comprises: filler opening (P), return opening (T), the first actuator port (A) and the second actuator port (B), 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);
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 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:
In the first operative state, filler opening (P) communicates with the first actuator port (A), and return opening (T) communicates with the second actuator port (B);
In a second operative state, filler opening (P), return opening (T), the first actuator port (A) and the second actuator port (B) all end, or filler opening (P) communicates with return opening (T), the first actuator port (A) and the second actuator port (B) cut-off;
Under the 3rd working state, filler opening (P) communicates with the second actuator port (B), and return opening (T) communicates with the first actuator port (A).
4. rotary control valve group according to claim 3, is characterized in that, described proportional reversing valve (2) is hydraulic control proportional reversing valve.
5. rotary control valve group according to claim 3, is characterized in that, also comprise:
First relief valve (41), its filler opening communicates with the first actuator port (A), and 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 overflow hydraulic fluid port communicates with the first actuator port (A).
6. rotary control valve group according to claim 5, is characterized in that, also comprise:
First one-way valve (31), its oil outlet communicates with the first actuator port (A), and filler opening communicates with return opening (T);
Second one-way valve (32), its oil outlet communicates with the second actuator port (B), and filler opening communicates with return opening (T).
7. rotary control valve group according to claim 6, it is characterized in that, also comprise: back pressure valve (1), the oil outlet of the first one-way valve (31) and the oil outlet of the second one-way valve (32) are communicated with oil return circuit by described back pressure valve (1).
8. a revolution hydraulic control system, it is characterized in that, comprise: oil hydraulic pump, executive component and the rotary control valve group described in claim 1 to 7 any one, the filler opening (P) of the proportional reversing valve (2) of rotary control valve group communicates with the oil drain out of oil hydraulic pump, and the first actuator port (A) and the second actuator port (B) communicate with two actuator ports of described executive component respectively.
9. revolution hydraulic control system according to claim 8, 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 the revolution hydraulic control system described in claim 8 or 9.
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