CN103697000B - Realize the infinite variable speed hydraulic control system of actuator - Google Patents
Realize the infinite variable speed hydraulic control system of actuator Download PDFInfo
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- CN103697000B CN103697000B CN201310643364.7A CN201310643364A CN103697000B CN 103697000 B CN103697000 B CN 103697000B CN 201310643364 A CN201310643364 A CN 201310643364A CN 103697000 B CN103697000 B CN 103697000B
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Abstract
One realizes the infinite variable speed hydraulic control system of actuator, comprise metering pump, main valve, fuel tank, the first oil circuit, actuator and the second oil circuit, metering pump is connected with fuel tank, main valve is connected with metering pump, first oil circuit is provided with the first proportional reversing valve, and the second oil circuit is provided with the first switch valve, hydraulic control system also comprises speed Control oil circuit, speed Control oil circuit connects the control mouth of the first proportional reversing valve, speed Control oil circuit is connected with proportional pressure-reducing valve and pilot control, proportional pressure-reducing valve is connected between the control mouth of the first proportional reversing valve and pilot control, the guide oil of pilot control arrives the control mouth of the first proportional reversing valve through proportional pressure-reducing valve, the pilot pressure that proportional pressure-relief valve control is applied on the control mouth of the first proportional reversing valve gradually changes between lower limit and CLV ceiling limit value, first proportional reversing valve is correspondingly controlled to be in cut-off completely and the diverse location completely between conducting.The present invention's metering pump can realize the stepless change of actuator.
Description
Technical field
The present invention relates to hydraulic control system, particularly relate to one and realize the infinite variable speed hydraulic control system of actuator.
Background technique
At present, engineering machinery is more and more towards high efficiency, high-power, large-tonnage, highi degree of accuracy, the future development such as steady.Engineering machinery, for raising the efficiency, generally adopts composite move, such as turn round, be elevated, equipment work (for continuous wall trench machine, its equipment for grab bucket, grab bucket need opening and closing) etc.Wherein, with the rotation motion of engineering machinery, because rotary inertia is larger, car body shaking amplitude is comparatively large, particularly in pivotal process, in startup and anxious stopping time, easily impact phenomenon that is comparatively large, galloping, this just needs swirl gear can realize stepless speed regulation control.
Referring to Fig. 1, is a kind of existing hydraulic control system being applied to swirl gear, it comprise rotary reducer 11, break 12, motor 13, sequence valve 14,15, equilibrium valve 16,17 and brake circuit 18.Described motor 13 drives rotary reducer 11 to rotate, and described break 12 is for braking the rotation of motor 13.Described swirl gear also comprises the first working oil path 19a and the second working oil path 19b, described first working oil path 19a connects the actuator port A of main valve (not shown) and one end of motor 13, and described second working oil path 19b connects the actuator port B of main valve and the other end of motor 13.Described sequence valve 14,15 is connected between the two ends of motor 13 separately, and two sequence valve 14,15 Opposite direction connections.Described equilibrium valve 16,17 is separately positioned on described first working oil path 19a and the second working oil path 19b.Described brake circuit 18 is connected on described first working oil path 19a and the second working oil path 19b by shuttle valve, with by the pressure oil on described first working oil path 19a or the second working oil path 19b to break 12 brake off.When actuator port A fuel feeding, the one-way valve of pressure oil in equilibrium valve 16 carries out fuel feeding to the left end of motor 13, and the pressure oil that actuator port A provides simultaneously can open the sequence valve of equilibrium valve 17, thus opens oil circuit, i.e. the second working oil path 19b, realizes motor 13 oil return smoothly.Described sequence valve 14,15 is overflow Protective valve, plays effect that is shock-resistant and overload protection.
In above-mentioned swirl gear, for realizing stepless speed regulation, general employing variable displacement pump is hydraulic system fuel feeding, realizes speed governing by changing pump delivery, and for ensureing the stability of hydraulic system, need the main valve of employing, variable displacement pump, guide proportion control valve often expensive; In addition, because engineering machinery tonnages a lot of is at present larger, therefore its rotary inertia is larger, therefore turn round startup, that the anxious stopping time will cause engineering machinery entirety to rock will be larger, affect working life, and cause more greatly hydraulic shock also comparatively large due to rotary inertia, can the linkage structure of mechanism member of spoiled work machinery.
Summary of the invention
In view of the above, be necessary to provide a kind of and realize the infinite variable speed hydraulic control system of actuator without the need to what adopt variable displacement pump.
One realizes the infinite variable speed hydraulic control system of actuator, comprise metering pump, main valve, fuel tank, first oil circuit, actuator, and second oil circuit, the filler opening of described metering pump is connected with described fuel tank, described main valve is connected with the oil outlet of described metering pump, described main valve has the first actuator port and the second actuator port, described first oil circuit connects one end of described first actuator port and described actuator, described second oil circuit connects the other end of described second actuator port and described actuator, described first oil circuit is provided with the first proportional reversing valve, described second oil circuit is provided with the first switch valve, described hydraulic control system also comprises speed Control oil circuit, described speed Control oil circuit connects the control mouth of described first proportional reversing valve, described speed Control oil circuit is connected with proportional pressure-reducing valve and pilot control, between the control mouth that described proportional pressure-reducing valve is connected to described first proportional reversing valve and described pilot control, the guide oil of described pilot control arrives the control mouth of described first proportional reversing valve through described proportional pressure-reducing valve, the pilot pressure that described proportional pressure-relief valve control is applied on the control mouth of described first proportional reversing valve gradually changes between lower limit and CLV ceiling limit value, described first proportional reversing valve is correspondingly controlled to be in cut-off completely and the diverse location completely between conducting.
Further, described hydraulic control system also comprises three oil circuit in parallel with described first oil circuit and four oil circuit in parallel with described second oil circuit, described 3rd oil circuit is provided with second switch valve, described 4th oil circuit is provided with the second proportional reversing valve, described speed Control oil circuit also connects the control mouth of described second proportional reversing valve, described speed Control oil circuit is also connected with selector valve, described selector valve is connected with described proportional pressure-reducing valve, described selector valve has two actuator ports, two actuator ports of described selector valve are connected with the control mouth of described second proportional reversing valve with the control mouth of described first proportional reversing valve respectively.
Further, described selector valve is 3-position 4-way pilot operated directional control valve, described selector valve has the first control mouth and second and controls mouth, first of described selector valve controls mouth and to be connected on described first oil circuit and to be connected between described first proportional reversing valve and described first actuator port, second of described selector valve controls mouth and to be connected on described 4th oil circuit and to be connected between described second proportional reversing valve and described second actuator port, the filler opening of described selector valve is connected with the oil outlet of described proportional pressure-reducing valve, and the return opening of described selector valve is connected with fuel tank.
Further, first of described selector valve controls to be provided with the first one-way throttle valve between mouth and described first oil circuit, second of described selector valve controls to be provided with the second one-way throttle valve between mouth and described 4th oil circuit, one-way valve in described first one-way throttle valve allows fluid to flow to described first oil circuit from described selector valve, and the one-way valve in described second one-way throttle valve allows fluid to flow to described 4th oil circuit from described selector valve.
Further, described first switch valve and second switch valve are 2/2-way hydraulic control valve, first of described first switch valve controls mouth and is all connected with described first oil circuit with the second control mouth of described second switch valve, and second of described first switch valve controls mouth and is all connected with described 4th oil circuit with the first control mouth of described second switch valve; When described first switch valve is controlled to be in cut-off or the first state of conducting, described second switch valve is in the second contrary state by control.
Further, first of described first switch valve controls second of mouth and described second switch valve and controls mouth and to be all connected on described first oil circuit and to be connected between described first proportional reversing valve and described first actuator port, and second of described first switch valve controls first of mouth and described second switch valve and controls mouth and to be all connected on described 4th oil circuit and to be connected between described second proportional reversing valve and described second actuator port.
Further, described hydraulic control system also comprises the first one-way valve, the second one-way valve and relief valve, described first one-way valve and the second one-way valve are in parallel with described actuator again after connecting, the filler opening of described relief valve is connected between the first one-way valve and the second one-way valve, the oil outlet of described relief valve connects fuel tank, described first one-way valve is installed in the mode allowing fluid and flow to described relief valve from described first oil circuit, and described second one-way valve is installed in the mode allowing fluid and flow to described relief valve from described 4th oil circuit.
Further, described hydraulic control system also comprises the 3rd one-way valve and the 4th one-way valve, described 3rd one-way valve and the 4th one-way valve are in parallel with described actuator again after connecting, fuel tank is connected between described 3rd one-way valve and the 4th one-way valve, described 3rd one-way valve is installed in the mode allowing fluid and flow to described first oil circuit from fuel tank, and described 4th one-way valve is installed in the mode allowing fluid and flow to described 4th oil circuit from fuel tank.
Further, described hydraulic control system also comprises brake circuit, described brake circuit is provided with break and selector valve, the filler opening of described selector valve is connected with described first oil circuit and described 4th oil circuit, the oil outlet of described selector valve is connected with the oil pocket of described break, and described selector valve is alternatively communicated with described first oil circuit or described 4th oil circuit.
Further, described proportional pressure-reducing valve comprises electric control handle, and the aperture of described electric control handle is directly proportional to the delivery pressure of described proportional pressure-reducing valve.
Compared to prior art, the setting of passing ratio reduction valve of the present invention and proportional reversing valve, adopts metering pump can realize the stepless change of actuator, reduces cost to a certain extent.The delivery pressure of control ratio reduction valve can be carried out by electric control handle, proportional reversing valve is made to be open at arbitrary position, corresponding proportional reversing valve aperture minimum state during the minimum aperture of handle, corresponding proportional reversing valve aperture maximum rating during handle maximum opening, and along with the increase of handle aperture, the aperture of proportional reversing valve also increases gradually, realizes, to the stepless speed regulation of swirl gear, simplifying control mode.Start and the anxious stopping time in actuator, open degree due to proportional reversing valve has one from the large process (i.e. open time delay) of little change, can compensator or trimmer pressure, when completely opened, the output in full of flow can be accomplished again, too much can not increase the pressure loss of whole oil circuit.Because proportional pressure-reducing valve can adopt electric control handle to control, for reducing the anxious impact stopping bringing, when the requirement without the need to realizing location, electric ratio handle return can be made slowly, reduce hydraulic shock, realizing buffering when stopping; When needs are located, make handle returning quickly, the anxious stopping time realizes location fast.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the hydraulic control system of the swirl gear of prior art; And
Fig. 2 is the schematic diagram realizing the infinite variable speed hydraulic control system of actuator of the embodiment of the present invention.
Embodiment
By describing technology contents of the present invention, structure characteristics in detail, realized object and effect, accompanying drawing is coordinated to be explained in detail below in conjunction with mode of execution.
Refer to Fig. 2, the infinite variable speed hydraulic control system of actuator that realizes of the present invention comprises the first actuator port C, the second actuator port D, the first oil circuit 20, actuator 30, second oil circuit 40 and speed Control oil circuit 50.Described first actuator port C and the second actuator port D are connected with to actuator 30 fuel feeding with oil supply system 90.Described first oil circuit 20 connects one end of described first actuator port C and described actuator 30 respectively, and the first oil circuit 20 is provided with the first proportional reversing valve 22; Described second oil circuit 40 connects the other end of described second actuator port D and described actuator 30 respectively, and the second oil circuit 40 is provided with the first switch valve 42 to control the break-make of the second oil circuit 40.Described speed Control oil circuit 50 connects the control mouth of described first proportional reversing valve 22, described speed Control oil circuit 50 is connected with proportional pressure-reducing valve 55 and pilot control 58, wherein between the proportional pressure-reducing valve 55 control mouth that is connected to the first proportional reversing valve 22 and pilot control 58.
In above-mentioned hydraulic control system, the delivery pressure of speed Control oil circuit 50 described in proportional pressure-reducing valve 55 adjustable, the pilot pressure realizing the control mouth of adjustment first proportional reversing valve 22 gradually changes between lower limit and CLV ceiling limit value, and (wherein lower limit can be zero, CLV ceiling limit value is force value required when the first proportional reversing valve 22 can be opened completely, concrete characteristic according to proportional reversing valve and determine), and then make the first proportional reversing valve 22 correspondingly be controlled to be in cut-off completely and the different position completely between conducting, reach the restriction size of adjustment first proportional reversing valve 22 and the object of through-current capacity.Like this, the oil mass entering actuator 30 from the first oil circuit 20 also just changes thereupon, achieves the stepless speed regulation to actuator 30.Meanwhile, described first switch valve 42 is opened, and the fluid of described actuator 30 the other end flows back to fuel tank by the second oil circuit 40.
Described actuator 30 can be motor or oil cylinder etc.Such as, when actuator 30 is motor, it can rotate and reverse, and therefore the two ends of actuator 30 all can be used as oil inlet end or oil outlet end; When actuator 30 is oil cylinder, it can be two-way cylinder, and therefore its rodless cavity and rod chamber all can be used as oil suction chamber or go out oil pocket.The motor being energy clockwise and anticlockwise for described actuator 30 is below illustrated, and described actuator 30 rotates for driving rotary reducer 31, thus realizes the rotation motion of engineering machinery.
Further, described stepless speed changing hydraulic control system also comprises three oil circuit 70 in parallel with the first oil circuit 20 and four oil circuit 60 in parallel with the second oil circuit 40, described 3rd oil circuit 70 is provided with second switch valve 72 to control the break-make of the 3rd oil circuit 70, described 4th oil circuit 60 is provided with the second proportional reversing valve 62, described speed Control oil circuit 50 also connects the control mouth of described second proportional reversing valve 62, described speed Control oil circuit 50 is also connected with selector valve 52, described selector valve 52 is connected with described proportional pressure-reducing valve 55, described selector valve 52 has two actuator ports, two actuator ports of described selector valve 52 are connected with the control mouth of described second proportional reversing valve 62 with the control mouth of described first proportional reversing valve 22 respectively, and described selector valve 52 optionally can be communicated with described first proportional reversing valve 22 or the second proportional reversing valve 62 when commutating, the delivery pressure of proportional pressure-reducing valve 55 is optionally applied on the control mouth of the first proportional reversing valve 22 or the second proportional reversing valve 62.
Further, described selector valve 52 is 3-position 4-way pilot operated directional control valve, described selector valve 52 has the first control mouth and second and controls mouth, two of described selector valve 52 control mouth and are connected on the first oil circuit 20 and the 4th oil circuit 60, the filler opening of described selector valve 52 is connected with the oil outlet of described proportional pressure-reducing valve 55, and the filler opening of described proportional pressure-reducing valve 55 is connected with described pilot control 58.When the first oil circuit 20 oil-feed, the left end pressure of selector valve 52 is greater than right-hand member pressure, selector valve 52 is in the primary importance of left position and is communicated with by the control mouth of proportional pressure-reducing valve 55 with the first proportional reversing valve 22, the control mouth flowing to the first proportional reversing valve 22 from the fluid of proportional pressure-reducing valve 55 makes the first proportional reversing valve 22 move to conduction position gradually from rest position, and increase gradually along with the delivery pressure of proportional pressure-reducing valve 55, the pilot pressure be applied on the control mouth of the first proportional reversing valve 22 also increases gradually, the restriction of the first proportional reversing valve 22 in turn on process also correspondingly increases gradually, flow increases gradually, the left end oil-feed of described actuator 30 is also rotated towards first direction, otherwise, when the 4th oil circuit 60 oil-feed, the right-hand member pressure of selector valve 52 is greater than left end pressure, selector valve 52 is in the second place of right position and is communicated with by the control mouth of proportional pressure-reducing valve 55 with the second proportional reversing valve 62, the control mouth flowing to the second proportional reversing valve 62 from the fluid of proportional pressure-reducing valve 55 makes the second proportional reversing valve 62 move to conduction position gradually from rest position, and increase gradually along with the delivery pressure of proportional pressure-reducing valve 55, the pilot pressure be applied on the control mouth of the second proportional reversing valve 62 also increases gradually, second proportional reversing valve 62 orifice size in turn on process increases gradually, flow increases gradually, then actuator 30 right-hand member oil-feed and rotate towards contrary second direction.Described selector valve 52 is when meta, two actuator ports of described selector valve 52 are all communicated with fuel tank, the filler opening of described selector valve 52 ends not oil-feed, described first proportional reversing valve 22 is directly communicated with and oil return with the return opening of selector valve 52 with the control mouth of the second proportional reversing valve 62, described first proportional reversing valve 22 and the second proportional reversing valve 62 are all in rest position, do not have pressure oil to supply described actuator 30, described actuator 30 is failure to actuate.
Further, first of described selector valve 52 controls mouth and to be connected on described first oil circuit 20 and to be connected between the first proportional reversing valve 22 and the first actuator port C, and second of described selector valve 52 controls mouth and to be connected on described 4th oil circuit 60 and to be connected between the second proportional reversing valve 62 and the second actuator port D.
Further, first of described selector valve 52 controls to be provided with the first one-way throttle valve 53a between mouth and the first oil circuit 20, second of described selector valve 52 controls to be provided with the second one-way throttle valve 53b between mouth and the 4th oil circuit 60, one-way valve in described first one-way throttle valve 53a allows fluid to flow to the first oil circuit 20 from selector valve 52, and the one-way valve in described second one-way throttle valve 53b allows fluid to flow to the 4th oil circuit 60 from selector valve 52.
Further, described switch valve 42,72 is 2/2-way hydraulic control valve, first of described first switch valve 42 controls mouth and is all connected with the first oil circuit 20 with the second control mouth of second switch valve 72, and second of described first switch valve 42 controls mouth and is all connected with the 4th oil circuit 60 with the first control mouth of second switch valve 72; When described first switch valve 42 is controlled to be in cut-off or the first state of conducting, described second switch valve 72 is in the second contrary state by control.When first of switch valve 42,72 control mouth have pressure oil time, described switch valve 42,72 becomes on state from cut-off state, when second of switch valve 42,72 control mouth have pressure oil time, described switch valve 42,72 becomes cut-off state from state.
Further, first of described first switch valve 42 controls second of mouth and second switch valve 72 and controls mouth and to be all connected on described first oil circuit 20 and to be connected between the first proportional reversing valve 22 and the first actuator port C, and second of described first switch valve 42 controls first of mouth and second switch valve 72 and controls mouth and to be all connected on described 4th oil circuit 60 and to be connected between the second proportional reversing valve 62 and the second actuator port D.
Further, described hydraulic control system also comprises the first one-way valve 23a, second one-way valve 23b and relief valve 24, described first one-way valve 23a and the second one-way valve 23b is in parallel with described actuator 30 again after connecting, the filler opening of described relief valve 24 is connected between the first one-way valve 23a and the second one-way valve 23b, the oil outlet of described relief valve 24 connects fuel tank, described first one-way valve 23a installs in the mode allowing fluid and flow to relief valve 24 from the first oil circuit 20, described second one-way valve 23a installs in the mode allowing fluid and flow to relief valve 24 from the 4th oil circuit 60.The first one-way valve 23a or the second one-way valve 23b can be opened when the induced pressure in two chambeies of actuator 30 exceedes predefined value, and by relief valve 24 overflow, thus play protection actuator 30, the effect that buffering hydraulic impacts.
Further, described hydraulic control system also comprises the 3rd one-way valve 25a and the 4th one-way valve 25b, described 3rd one-way valve 25a and the 4th one-way valve 25b is in parallel with described actuator 30 again after connecting, fuel tank is connected between described 3rd one-way valve 25a and the 4th one-way valve 25b, described 3rd one-way valve 25a installs in the mode allowing fluid and flow to the first oil circuit 20 from fuel tank, and described 4th one-way valve 25b installs in the mode allowing fluid and flow to the 4th oil circuit 60 from fuel tank.Described 3rd one-way valve 25a and the 4th one-way valve 25b can give the two ends repairing of actuator 30, thus prevents actuator 30 from inhaling sky.
Further, described hydraulic control system also comprises brake circuit 80, described brake circuit 80 is provided with break 81 and selector valve 82, the filler opening of described selector valve 82 is connected with described first oil circuit 20 and described 4th oil circuit 60 respectively, its oil outlet is connected with the oil pocket of described break 81, and described selector valve 82 is alternatively communicated with described first oil circuit 20 or the 4th oil circuit 60.Particularly, described selector valve 82 is shuttle valves, when the first oil circuit 20 and the 4th oil circuit 60 any one of them connect high pressure oil time, this high-pressure oil passage of shuttle valve conducting and break 81, high pressure oil is made to enter break 81 brake off, allow actuator 30 to operate, when the first oil circuit 20 and the 4th oil circuit 60 all do not connect high pressure oil, break 81 pairs of actuators 30 brake.Break 81 can be brake cylinder.
Further, described brake circuit 80 is also provided with pilot operated directional control valve 84, described pilot operated directional control valve 84 comprises cut-off and is communicated with two states, and the filler opening of described pilot operated directional control valve 84, oil outlet and control mouth are connected with the oil outlet of the oil outlet of described selector valve 82, break 81 and selector valve 82 respectively.When the first oil circuit 20 and the 4th oil circuit 60 all do not connect high pressure oil, described pilot operated directional control valve 84 is in cut-off state, and it can ensure that now break 81 is in braking state.When the arbitrary oil circuit in the first oil circuit 20 and the 4th oil circuit 60 connects high pressure oil, high pressure oil is switched to the control mouth of described pilot operated directional control valve 84 to open described pilot operated directional control valve 84, described pilot operated directional control valve 84 is made to be on state, it is brake cylinder in the present embodiment that high pressure oil arrives break 81(through described pilot operated directional control valve 84 and the reduction valve (figure does not mark) be positioned at after described pilot operated directional control valve 84), with the braking state of brake off device 81.In the present embodiment, conducting and the disconnection of described pilot operated directional control valve 84 by adopting the method for hydraulic control to control described pilot operated directional control valve 84, a kind of braking retardation effect can also be realized, namely set up in the process of certain oil pressure at the hydraulic control end of described pilot operated directional control valve 84, allow described actuator 30 within a certain period of time first fuel feeding open described break 81 again, prevent described break 81 prior to described actuator 30 brake off, and cause the mechanisms such as turntable to there is the uncertain motion states such as slippery.
Further, described hydraulic control system also comprises oil supply system 90, described oil supply system 90 comprises metering pump 91, main valve 92, relief valve 94 and fuel tank 96, described first actuator port C and the second actuator port D is the actuator port of main valve 92, described main valve 92 also comprises filler opening and return opening, described metering pump 91 is arranged between described filler opening and fuel tank 96, and described return opening is communicated with fuel tank, between the outlet that described relief valve 94 is connected to described metering pump 91 and described fuel tank 96; The filler opening of described main valve 92 is all optionally communicated with the first actuator port C or the second actuator port D with oil outlet.Particularly, described main valve 92 is three-position four-way electromagnetic directional valve, when main valve 92 is in primary importance, the first oil circuit 20 fuel feeding given by metering pump 91, when main valve 92 is positioned at the second place, the 4th oil circuit 60 fuel feeding given by metering pump 91, when main valve 92 is positioned at meta, and the direct oil sump tank of metering pump 91 oil out.
Further, described proportional pressure-reducing valve 55 comprises electric control handle, and the aperture of described electric control handle is directly proportional to the delivery pressure of described proportional pressure-reducing valve 55, therefore controls the delivery pressure of described proportional pressure-reducing valve 55 by this electric control handle.For reducing the anxious impact stopping bringing, when the requirement without the need to realizing location, electric ratio handle return can be made slowly, reduce hydraulic shock, realizing buffering when stopping; When needs are located, make handle returning quickly, the anxious stopping time realizes location fast.
When the first oil circuit 20 fuel feeding given by metering pump 91, main valve 92 is in primary importance, the left position namely shown in Fig. 2, and the filler opening of main valve 92 is communicated with described first actuator port C, the return opening of main valve 92 is communicated with described second actuator port D, and the first oil circuit 20 fuel feeding given by metering pump 91.Second pressure controlling mouth (left end namely in Fig. 2) of described second switch valve 72 is greater than its first control mouth (right-hand member namely in Fig. 2), second switch valve 72 is in the rest position of left position, makes the pressure oil in the first oil circuit 20 can only lead to actuator 30 by the first proportional reversing valve 22.The pressure at the first one-way throttle valve 53a place is greater than the second one-way throttle valve 53b, first of the left end of selector valve 52 the pressure controlling mouth is made to be greater than the pressure of the second control mouth of right-hand member, so selector valve 52 commutates to left position, the oil outlet of proportional pressure-reducing valve 55 is communicated with the control mouth of the first proportional reversing valve 22, the control mouth of the second proportional reversing valve 62 is communicated with fuel tank, the guide oil of pilot control 58 arrives the control mouth of the first proportional reversing valve 22 through proportional pressure-reducing valve 55, the delivery pressure of proportional pressure-reducing valve 55 is changed by the curtage (by handling its electric control handle to realize) changing proportional pressure-reducing valve 55, thus change the pressure be applied on the control mouth of the first proportional reversing valve 22, make the first proportional reversing valve 22 by the diverse location controlling to be in from ending completely to complete conducting, and along with the pilot pressure change be applied on the control mouth of the first proportional reversing valve 22, also (minimum be zero to the respective change of the restriction size of the first proportional reversing valve 22, be full flow to the maximum), thus realize stepless speed regulation.Simultaneously, first of first switch valve 42 controls mouth (left end namely shown in Fig. 2) owing to connecting with the first oil circuit 20, its pressure is greater than second of the first switch valve 42 and controls mouth (right-hand member namely shown in Fig. 2), so the first switch valve 42 is in the conduction position of left position, the fluid of actuator 30 right-hand member is through the second oil circuit 40 oil return.In addition, the high pressure oil of the first oil circuit 20 also enters break 81 through selector valve 82 and pilot operated directional control valve 84, the braking of brake off device 81, allows actuator 30 to operate.
When the 4th oil circuit 60 fuel feeding given by metering pump 91, main valve 92 is in the second place, the right position namely shown in Fig. 2, and the filler opening of main valve 92 is communicated with described second actuator port D, the return opening of main valve 92 is communicated with described first actuator port C, and the 4th oil circuit 60 fuel feeding given by metering pump 91.Second pressure controlling mouth (right-hand member namely in Fig. 2) of described first switch valve 42 is greater than its first control mouth (left end namely in Fig. 2), first switch valve 42 is in the rest position of right position, makes the pressure oil in the 4th oil circuit 60 can only lead to actuator 30 by the second proportional reversing valve 62.The pressure at the second one-way throttle valve 53b place is greater than the first one-way throttle valve 53a, second of the right-hand member of selector valve 52 the pressure controlling mouth is made to be greater than the pressure of the first control mouth of left end, so selector valve 52 commutates to right position, the oil outlet of proportional pressure-reducing valve 55 is communicated with the control mouth of the second proportional reversing valve 62, the control mouth of the first proportional reversing valve 22 is communicated with fuel tank, the guide oil of pilot control 58 arrives the control mouth of the second proportional reversing valve 62 through proportional pressure-reducing valve 55, the delivery pressure of proportional pressure-reducing valve 55 is changed by the curtage (by handling its electric control handle to realize) changing proportional pressure-reducing valve 55, thus change the pressure be applied on the control mouth of the second proportional reversing valve 62, make the second proportional reversing valve 62 by the diverse location controlling to be in from ending completely to complete conducting, and along with the pilot pressure change be applied on the control mouth of the second proportional reversing valve 62, also (minimum be zero to the respective change of the restriction size of the second proportional reversing valve 62, be full flow to the maximum), thus realize stepless speed regulation.Simultaneously, first of second switch valve 72 controls mouth (right-hand member namely shown in Fig. 2) owing to connecting with the 4th oil circuit 60, its pressure is greater than second of second switch valve 72 and controls mouth (left end namely shown in Fig. 2), so second switch valve 72 is in the conduction position of right position, the fluid of actuator 30 left end is through the 3rd oil circuit 70 oil return.In addition, the high pressure oil of the 4th oil circuit 60 also enters break 81 through selector valve 82 and pilot operated directional control valve 84, the braking of brake off device 81, allows actuator 30 to operate.
Utilize hydraulic control system of the present invention, adopt metering pump 91 can realize the stepless change of actuator 30, reduce cost to a certain extent.The delivery pressure of control ratio reduction valve 55 can be carried out by electric control handle, proportional reversing valve 22,62 is made to be open at arbitrary position, corresponding proportional reversing valve 22,62 aperture minimum state during the minimum aperture of handle, corresponding proportional reversing valve 22,62 aperture maximum rating during handle maximum opening, and along with the increase of handle aperture, the aperture of proportional reversing valve 22,62 also increases gradually, realizes, to the stepless speed regulation of swirl gear, simplifying control mode.Start and the anxious stopping time in actuator 30, open degree due to proportional reversing valve 22,62 has one from the large process (i.e. open time delay) of little change, can compensator or trimmer pressure, when completely opened, the output in full of flow can be accomplished again, too much can not increase the pressure loss of whole oil circuit.Because proportional pressure-reducing valve 55 can adopt electric control handle to control, for reducing the anxious impact stopping bringing, when the requirement without the need to realizing location, electric ratio handle return can be made slowly, reduce hydraulic shock, realizing buffering when stopping; When needs are located, make handle returning quickly, the anxious stopping time realizes location fast.
In this article, term " comprises ", " comprising " or its any other variant are intended to contain comprising of nonexcludability, except comprising those listed key elements, but also can comprise other key elements clearly do not listed.
In this article, the involved noun of locality such as forward and backward, upper and lower is arranged in figure with component in accompanying drawing and component position each other defines, clear and convenient just in order to expression technology scheme.Should be appreciated that the use of the described noun of locality should not limit the scope of the application's request protection.
In this article, unless otherwise specifically indicated, otherwise, sequence adjective " first ", " second " etc. for describing element be only used to distinguish similar elements, and do not mean that the element that describes like this must according to given order, or time, space, grade or other restriction.
When not conflicting, the feature in embodiment herein-above set forth and embodiment can be combined with each other.
The foregoing is only the preferred embodiments of the present invention; not thereby the scope of the claims of the present invention is limited; every equivalent structure transformation utilizing specification of the present invention and accompanying drawing content to do; or be directly or indirectly used in other relevant technical fields, be all in like manner included in scope of patent protection of the present invention.
Claims (10)
1. one kind realizes the infinite variable speed hydraulic control system of actuator, comprise metering pump (91), main valve (92), fuel tank (96), first oil circuit (20), actuator (30), and second oil circuit (40), the filler opening of described metering pump (91) is connected with described fuel tank (96), described main valve (92) is connected with the oil outlet of described metering pump (91), described main valve (92) has the first actuator port (C) and the second actuator port (D), described first oil circuit (20) connects one end of described first actuator port (C) and described actuator (30), described second oil circuit (40) connects the other end of described second actuator port (D) and described actuator (30), it is characterized in that: described first oil circuit (20) is provided with the first proportional reversing valve (22), described second oil circuit (40) is provided with the first switch valve (42), described hydraulic control system also comprises speed Control oil circuit (50), described speed Control oil circuit (50) connects the control mouth of described first proportional reversing valve (22), described speed Control oil circuit (50) is connected with proportional pressure-reducing valve (55) and pilot control (58), between the control mouth that described proportional pressure-reducing valve (55) is connected to described first proportional reversing valve (22) and described pilot control (58), the guide oil of described pilot control (58) arrives the control mouth of described first proportional reversing valve (22) through described proportional pressure-reducing valve (55), described proportional pressure-reducing valve (55) controls the pilot pressure be applied on the control mouth of described first proportional reversing valve (22) and gradually changes between lower limit and CLV ceiling limit value, described first proportional reversing valve (22) is correspondingly controlled to be in cut-off completely and the diverse location completely between conducting.
2. hydraulic control system according to claim 1, it is characterized in that: described hydraulic control system also comprises three oil circuit (70) in parallel with described first oil circuit (20) and four oil circuit (60) in parallel with described second oil circuit (40), described 3rd oil circuit (70) is provided with second switch valve (72), described 4th oil circuit (60) is provided with the second proportional reversing valve (62), described speed Control oil circuit (50) also connects the control mouth of described second proportional reversing valve (62), described speed Control oil circuit (50) is also connected with selector valve (52), described selector valve (52) is connected with described proportional pressure-reducing valve (55), described selector valve (52) has two actuator ports, two actuator ports of described selector valve (52) are connected with the control mouth of described second proportional reversing valve (62) with the control mouth of described first proportional reversing valve (22) respectively.
3. hydraulic control system according to claim 2, it is characterized in that: described selector valve (52) is 3-position 4-way pilot operated directional control valve, described selector valve (52) has the first control mouth and second and controls mouth, first control mouth of described selector valve (52) is connected to described first oil circuit (20) and goes up and be connected between described first proportional reversing valve (22) and described first actuator port (C), second control mouth of described selector valve (52) is connected to described 4th oil circuit (60) and goes up and be connected between described second proportional reversing valve (62) and described second actuator port (D), the filler opening of described selector valve (52) is connected with the oil outlet of described proportional pressure-reducing valve (55), the return opening of described selector valve (52) is connected with fuel tank.
4. hydraulic control system according to claim 3, it is characterized in that: first of described selector valve (52) controls to be provided with the first one-way throttle valve (53a) between mouth and described first oil circuit (20), second of described selector valve (52) controls to be provided with the second one-way throttle valve (53b) between mouth and described 4th oil circuit (60), one-way valve in described first one-way throttle valve (53a) allows fluid to flow to described first oil circuit (20) from described selector valve (52), one-way valve in described second one-way throttle valve (53b) allows fluid to flow to described 4th oil circuit (60) from described selector valve (52).
5. hydraulic control system according to claim 2, it is characterized in that: described first switch valve (42) and second switch valve (72) are 2/2-way hydraulic control valve, first of described first switch valve (42) controls mouth and is all connected with described first oil circuit (20) with the second control mouth of described second switch valve (72), and second of described first switch valve (42) controls mouth and is all connected with described 4th oil circuit (60) with the first control mouth of described second switch valve (72); When described first switch valve (42) is controlled to be in cut-off or the first state of conducting, described second switch valve (72) is in the second contrary state by control.
6. hydraulic control system according to claim 5, it is characterized in that: first of described first switch valve (42) controls second of mouth and described second switch valve (72) and controls mouth to be all connected to described first oil circuit (20) upper and be connected between described first proportional reversing valve (22) and described first actuator port (C), second of described first switch valve (42) controls first of mouth and described second switch valve (72) and controls mouth and be all connected to described 4th oil circuit (60) above and be connected between described second proportional reversing valve (62) and described second actuator port (D).
7. according to the hydraulic control system in claim 2-6 described in any one, it is characterized in that: described hydraulic control system also comprises the first one-way valve (23a), second one-way valve (23b) and relief valve (24), described first one-way valve (23a) and the second one-way valve (23b) are in parallel with described actuator (30) again after connecting, the filler opening of described relief valve (24) is connected between the first one-way valve (23a) and the second one-way valve (23b), the oil outlet of described relief valve (24) connects fuel tank, described first one-way valve (23a) is installed in the mode allowing fluid and flow to described relief valve (24) from described first oil circuit (20), described second one-way valve (23a) is installed in the mode allowing fluid and flow to described relief valve (24) from described 4th oil circuit (60).
8. hydraulic control system according to claim 7, it is characterized in that: described hydraulic control system also comprises the 3rd one-way valve (25a) and the 4th one-way valve (25b), described 3rd one-way valve (25a) and the 4th one-way valve (25b) are in parallel with described actuator (30) again after connecting, fuel tank is connected between described 3rd one-way valve (25a) and the 4th one-way valve (25b), described 3rd one-way valve (25a) is installed in the mode allowing fluid and flow to described first oil circuit (20) from fuel tank, described 4th one-way valve (25b) is installed in the mode allowing fluid and flow to described 4th oil circuit (60) from fuel tank.
9. according to the hydraulic control system in claim 2-6 described in any one, it is characterized in that: described hydraulic control system also comprises brake circuit (80), described brake circuit (80) is provided with break (81) and selector valve (82), the filler opening of described selector valve (82) is connected with described first oil circuit (20) and described 4th oil circuit (60), the oil outlet of described selector valve (82) is connected with the oil pocket of described break (81), described selector valve (82) is alternatively communicated with described first oil circuit (20) or described 4th oil circuit (60).
10. according to the hydraulic control system in claim 1-6 described in any one, it is characterized in that: described proportional pressure-reducing valve (55) comprises electric control handle, the aperture of described electric control handle is directly proportional to the delivery pressure of described proportional pressure-reducing valve (55).
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