CN103522896B - Front wheel auxiliary drive system of land leveller - Google Patents
Front wheel auxiliary drive system of land leveller Download PDFInfo
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- CN103522896B CN103522896B CN201310323675.5A CN201310323675A CN103522896B CN 103522896 B CN103522896 B CN 103522896B CN 201310323675 A CN201310323675 A CN 201310323675A CN 103522896 B CN103522896 B CN 103522896B
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Abstract
The invention discloses a kind of front wheel auxiliary drive system of land leveller, belong to engineering machinery field.When the invention solves existing one-pump two-motor driving front-wheel assistive drive certain side propulsive effort is easily lost, straight-line travelling is comparatively hard to keep, more difficult realization turns to the problems such as differential control.The main points of its technical scheme are: comprise driving engine, change speed gear box, assistive drive hydraulic efficiency pressure system and hydraulic control system, assistive drive hydraulic efficiency pressure system comprises integrated pressure shutoff valve, load-sensing valve, controllable capacity pump, reducing valve, solenoid directional control valve, left and right motor, shuttle valve, the flow regulating valve that oil circuit communicates, this hydraulic efficiency pressure system also comprises electro-hydraulic proportion reversing valve and flow divider valve, and hydraulic control system comprises drive pattern select switch, front-wheel assistive drive speed adjustment knob.The present invention is mainly used on road grader, the a11wheel drive that the front-wheel that can realize increasing road grader tractive force is assisted and avoid back-wheel drive to the front-wheel individual drive of the damage of road pavement planeness during meticulous leveling operation.
Description
Technical field
The present invention relates to a kind of Construction Machinery System, specifically, particularly relate to a kind of front wheel auxiliary drive system of land leveller.
Background technology
Road grader is typical towed Work machine, and equipment promotes by the tractive force of machine walking, and in the prior art, most of road grader adopts back axle wheel to drive, and propons only possesses turning function and do not drive tractive force.So road grader tractive force limit only determined by back axle wheel load and adhesion value, because load per axle before road grader generally accounts for about 30% of complete machine weight, so road grader has about 30% tractive force not played.And when the meticulous leveling operation operating mode of road grader, road pavement flatness requirement is higher, common back-wheel drive may be excessive and form rut on smooth-riding surface due to back-wheel drive moment when meticulous leveling operation, road pavement planeness causes damage, front-wheel individual drive pattern then avoids the generation of this kind of phenomenon, and under front-wheel individual drive pattern, trailing wheel is neutral gear position, complete machine is towed by front-wheel, and trailing wheel the road surface of the smooth mistake of road pavement can not cause damage.
For meeting road grader operating needs under different operating mode, front-wheel assistive drive can realize a11wheel drive pattern and front-wheel individual drive pattern solves the problem.For front-wheel assistant drive system and control thereof, in prior art form, a kind of employing double pump+double motor type of drive, when double pump+double motor scheme can solve that front-wheel load in left and right does not wait in some cases (during as slope operation) left and right motor rotary speed can be caused not wait thus be difficult to ensure road grader straight-line travelling problem, and when meeting turning by the two capacity of pump of regulable control about the different flow of front-wheel and pressure demand, but control for realizing double pump different displacements when wheel is turned, need to increase front-wheel steering angle sensor and articulation steering angular transducer, relative one-pump two-motor driving type of drive simultaneously, increase a driving pump, so cost relatively high and control more complicated.The second adopts one-pump two-motor driving scheme, as shown in Figure 1, because motor adopts parallel way, the very difficult guarantee road grader straight-line travelling problem that can cause left and right motor rotary speed not etc. when left and right front-wheel load does not wait, simultaneously poor at certain side front vehicle wheel adhesion value, when occurring skidding, skidding side motor assignment of traffic is easily caused too much to exceed the speed limit, and other single wheel is without driving, cause the forfeiture driving tractive force, and when turning to, turn to inboard wheel rotating speed low, resistance wheel is larger, and turn to outboard wheels rotating speed fast, resistance wheel is less, required flow is different, because left and right motor is in parallel.Left and right motor pressure is identical, and about when causing turning, front-wheel is more difficult realizes differential.
Summary of the invention
The object of the invention is to provide a kind of front wheel auxiliary drive system of land leveller, to overcome the defect that in prior art, front wheel auxiliary drive system of land leveller exists.
The present invention is achieved by the following technical solutions: a kind of front wheel auxiliary drive system of land leveller comprises driving engine, change speed gear box, assistive drive hydraulic efficiency pressure system and hydraulic control system, described assistive drive hydraulic efficiency pressure system comprises the integrated pressure shutoff valve that oil circuit communicates, load-sensing valve, controllable capacity pump, reducing valve, solenoid directional control valve, left, right motor, shuttle valve, flow regulating valve, described integrated pressure shutoff valve is connected with driving engine by jackshaft with the controllable capacity pump of load-sensing valve, left, right motor is left with road grader respectively, off front wheel connects, and this hydraulic efficiency pressure system also comprises electro-hydraulic proportion reversing valve and flow divider valve, left, the A of right motor, B mouth is directly communicated with fuel tank by two check valves of flow divider valve and the meta of electro-hydraulic proportion reversing valve, and described hydraulic control system comprises drive pattern select switch, front-wheel assistive drive speed adjustment knob, can be adjusted the control electric current of electro-hydraulic proportion reversing valve, realize the adjustment of front-wheel individual drive hourly velocity by front-wheel assistive drive speed adjustment knob.
This hydraulic efficiency pressure system also comprises electromagnetic proportion relief valve, and described hydraulic control system also comprises the front-wheel assistive drive tractive force knob driving tractive force to regulate when can realize front-wheel individual drive.
Drive pattern select switch has back-wheel drive pattern, the a11wheel drive pattern of front-wheel assistive drive and the Three models of front-wheel individual drive.
Left and right motor is Double-discharge radial plunger piston motor.
Compared with prior art, the invention has the beneficial effects as follows:
(1) according to front-wheel assistive drive of the present invention and control system thereof, road grader can realize back-wheel drive pattern, the a11wheel drive pattern of front-wheel assistive drive and the Three models of front-wheel individual drive respectively according to operating mode, improve operating efficiency, effectively road grader tractive force is improved in the a11wheel drive pattern of front-wheel assistive drive, expand the range of use of road grader, in front-wheel individual drive pattern, be conducive to meticulous leveling operation, reduce the damage of road pavement planeness.
(2) compare existing double pump+double motor assistive drive, front-wheel auxiliary driving structure of the present invention simply, cost is lower, control is relatively simple.
(3) existing one-pump two-motor driving front-wheel assistive drive is compared, front-wheel assistive drive described in this patent solves current existing one-pump two-motor driving due to the very difficult guarantee road grader straight-line travelling problem that can cause left and right motor rotary speed not etc. when left and right front-wheel load does not wait, when the poor appearance of certain side front vehicle wheel adhesion value is skidded, skidding side motor assignment of traffic is easily caused too much to exceed the speed limit, and single wheel is without driving in addition, when causing the forfeiture of driving tractive force and turn, left and right front-wheel is more difficult realizes the problems such as differential.
Accompanying drawing explanation
Fig. 1 is the front-wheel assistive drive schematic diagram of prior art one-pump two-motor driving scheme;
Fig. 2 is front-wheel assistive drive schematic diagram of the present invention;
Fig. 3 is the I portion enlarged drawing of Fig. 2;
Fig. 4 is that front-wheel assistive drive of the present invention realizes back-wheel drive pattern, a11wheel drive pattern and front-wheel individual drive pattern diagram.
In figure, 1, controllable capacity pump; 2, servo plunger case; 3, pressure shut-off valve; 4, load-sensing valve; 5, electro-hydraulic reversing valve; 6, shuttle valve; 7, Double-discharge radial plunger piston motor; 8, electromagnetic valve change-over valve; 9, flow regulating valve; 10, reducing valve controllable capacity pump; 110, controllable capacity pump; 111, servo plunger case; 112, pressure shut-off valve; 113, load-sensing valve; 114, electromagnetic proportion relief valve; 115, reducing valve; 116, solenoid directional control valve; 117, flow divider valve; 118, left Double-discharge radial plunger piston motor; 119, right Double-discharge radial plunger piston motor; 120, flow regulating valve; 121, shuttle valve; 122, electro-hydraulic proportion reversing valve; 123, back-wheel drive pattern; 124, drive pattern select switch; 125, the a11wheel drive pattern of front-wheel assistive drive; 126, front-wheel individual drive pattern; 127, front-wheel assistive drive speed adjustment knob; 128, front-wheel assistive drive tractive force knob.
Detailed description of the invention
Below in conjunction with accompanying drawing, the invention will be further described:
As shown in Figure 1, in prior art, one-pump two-motor driving scheme adopts parallel way due to motor, the very difficult guarantee road grader straight-line travelling problem that can cause left and right motor rotary speed not etc. when left and right front-wheel load does not wait, simultaneously poor at certain side front vehicle wheel adhesion value, when occurring skidding, skidding side motor assignment of traffic is easily caused too much to exceed the speed limit, and other single wheel is without driving, cause the forfeiture driving tractive force, and when turning to, turn to inboard wheel rotating speed low, resistance wheel is larger, and turn to outboard wheels rotating speed fast, resistance wheel is less, required flow is different, because left and right motor is in parallel.This one-pump two-motor driving front-wheel assistant drive system left and right motor pressure is identical, and about when causing turning, front-wheel is more difficult realizes differential, but double pump+double motor scheme cost is lower relatively.
As Fig. 2, shown in Fig. 3, front wheel auxiliary drive system of land leveller comprises driving engine, change speed gear box, assistive drive hydraulic efficiency pressure system and hydraulic control system, assistive drive hydraulic efficiency pressure system comprises the integrated pressure shutoff valve 112 that oil circuit communicates, load-sensing valve 113, controllable capacity pump 110, reducing valve 115, solenoid directional control valve 116, left, right motor 118, 119, shuttle valve 121, flow regulating valve 120, pressure shut-off valve 112 is connected with driving engine by jackshaft with the controllable capacity pump 110 of load-sensing valve 113, left, right motor 118, 119 is left with road grader respectively, off front wheel connects, and this hydraulic efficiency pressure system also comprises electro-hydraulic proportion reversing valve 122, electromagnetic proportion relief valve 114 and flow divider valve 117, left, right motor 118, the A of 119, B mouth is directly communicated with fuel tank by two check valves of flow divider valve 117 and the meta of electro-hydraulic proportion reversing valve 122, and hydraulic control system comprises drive pattern select switch 124, front-wheel assistive drive speed adjustment knob 127, front-wheel assistive drive tractive force knob 128, the control electric current of electro-hydraulic proportion reversing valve 122 can be adjusted by front-wheel assistive drive speed adjustment knob 127, realize the adjustment of front-wheel individual drive hourly velocity, the control electric current of electromagnetic proportion relief valve 114 can be adjusted by front-wheel assistive drive tractive force knob 128, control the change of its pressure, when realizing front-wheel individual drive, drive the adjustment of tractive force, the left and right motor 118,119 of the present invention preferably adopts Double-discharge radial plunger piston motor.
As shown in Figure 4, drive pattern select switch 124 has the a11wheel drive pattern 125 of back-wheel drive pattern 123, front-wheel assistive drive and the Three models of front-wheel individual drive 126.
Under default mode of operation, drive pattern select switch 124 is positioned at back-wheel drive pattern 123 position, the now electromagnet D1 of solenoid directional control valve 116, electromagnet D2 and D3 of electro-hydraulic proportion reversing valve 122 is in power failure state, left, the A of right motor 118 and 119, B mouth is directly communicated with fuel tank by two check valves of flow divider valve 117 and the meta of electro-hydraulic proportion reversing valve 122, left, the radial plunger cam of right motor 118 and 119 presses down in piston spring effect gets back to plunger cavity, left, right motor 118 and 119 one-tenth free gear states, do not there is provided propulsive effort, road grader only wheel drive rearward.
When drive pattern select switch 124 is manually placed in front-wheel individual drive pattern 126, manual handling gearbox shifting handle is at meta, change speed gear box is not to rear wheel power, electro-hydraulic proportion reversing valve 122 electromagnet D2 obtains electric, the controllable capacity pump 110 of integrated pressure shutoff valve 112 and load-sensing valve 113 by jackshaft under driven by engine pressure oil output through electro-hydraulic proportion reversing valve 122 top, flow divider valve 117 flows to a left side, right motor 118 and 119, and then flow back to fuel tank through electro-hydraulic proportion reversing valve 122 top, simultaneously left, the load high pressure of right motor 118 and 119 feeds back to load-sensing valve 113 by shuttle valve 121, the delivery pressure of controllable capacity pump 110 and the difference of load pressure are set by the spring of load-sensing valve 113 and determined, before and after electro-hydraulic proportion reversing valve 122, pressure reduction is certain, can the size of current of electromagnetic valve D2 or D3 of corresponding adjustment electro-hydraulic proportion reversing valve 122 by front-wheel assistive drive speed adjustment knob 127, thus change the spool of electro-hydraulic proportion reversing valve 122 and the aperture position of valve body and size, and then change by flow divider valve 117 and a left side, the flow of right radial plunger piston motor 118 and 119, therefore realize a left side, the adjustment of the output speed of right radial plunger piston motor 118 and 119.
When setting front-wheel individual drive Speed Setting higher than a certain speed by front-wheel assistive drive speed adjustment knob 127, the D1 electromagnet of electromagnetic valve change-over valve 116 obtains electric, the pressure oil that now controllable capacity pump 110 exports reduces pressure through reducing valve 115 and arrives certain pressure, post-decompression pressure oil flows to the control port of left and right motor 118 and 119 respectively by solenoid directional control valve 116, and this pressure oil compresses the partial plunger cam retraction plunger cavity of left and right motor 118 and 119.Therefore left and right motor 118 and 119 is made to be in low displacement condition.Thus the output speed of left and right motor 118 and 119 can be improved when flow is constant.
The size of current of electromagnetic proportion relief valve 114 can be regulated by front-wheel assistive drive tractive force knob 128, thus the oil pressure relief of electromagnetic proportion relief valve 114 can be changed, because the pressure confinement of electromagnetic proportion relief valve 114 is left, load pressure size when right double motor 118 and 119 works, on a left side, when right motor 118 and 119 is in huge discharge or small displacement, when discharge capacity is certain, by changing the size of the pressure of electromagnetic proportion relief valve 114, can realize a left side, right motor 118 and 119 exports the size driving tractive force, thus according to applying working condition, the tractive force size of front-wheel assistive drive can be regulated, avoid because tractive force is greater than the tractive force that adhesion value determines, cause skidding and the inordinate wear of tire.
During front-wheel individual drive straight-line travelling (as shown in Figure 2), in normal conditions, pressure oil is by the pressure oil shunting etc. flow to left and right motor 118 and 119 of the meta of flow divider valve 117, simultaneously the pressure feedback of left motor 118 is to the upper end of flow divider valve 117, the pressure feedback of right motor 119 is to the lower end of flow divider valve 117, flow divider valve 117 is in meta state under feedback pressure, keep providing equal flow to left and right motor 118 and 119, thus ensure that left and right motor 118 is consistent with 119 output speeds, realize straight-line travelling.
During due to adhesion value change cause certain side motor drive power to be greater than tractive force that adhesive ability determines, skidding appears in this side motor, for left Double-discharge radial plunger piston motor 118, now the pressure of left Double-discharge radial plunger piston motor 118 is less than the load pressure of right Double-discharge radial plunger piston motor 119, flow divider valve 117 moves up at the pressure of left motor 118 and the pressure effect bottom spool of right motor 119, flow divider valve 117 is in bottom, the hydraulic fluid flow rate being diverted to left motor 118 is caused to reduce and oil pressure reduction through throttling action, and the hydraulic fluid flow rate flowing to right motor 119 increases and oil pressure increases, therefore left motor 118 output speed reduce while output torque reduce, avoid left wheel to skid to wear and tear, simultaneously the output speed of right motor 119 increase while output torque increase, improve output torque and the rotating speed of right motor 119, thus keep left, right motor 118 is consistent with 119 output speeds, keep the roadholding of road grader.Certain repairing can be provided to low pressure side motor by flow regulating valve 120, avoid the emptying phenomenon of low pressure side motor.When left and right wheel-borne load is different, little with left side wheel load, right side wheels load greatly arranges, and its service condition is similar to the above case, thus ensures the roadholding of road grader.
When road grader turns to, for right-hand turning to, now turn to the right wheel-borne load in inner side large, left outer wheel-borne load is little, the pressure of left motor 118 is less than the load pressure of right motor 119, flow divider valve 117 moves up at the pressure of left motor 118 and the pressure effect bottom spool of right motor 119, flow divider valve 117 is in bottom, the hydraulic oil pressure being diverted to left motor 118 is caused to reduce through throttling action, and the hydraulic oil pressure flowing to right motor 119 increases, therefore the output torque of left motor 118 reduces, and the output torque of right motor 119 increases, simultaneously right motor 119 by flow regulating valve 120 left motor 118 certain repairing is provided, thus ensure the flow needed for left motor 118 rotating speed, avoid the emptying phenomenon of low pressure side motor, realize the differential steering of road grader.
When road grader retreats, the D3 electromagnet of electro-hydraulic proportion reversing valve 122 obtains electric, the pressure oil that now controllable capacity pump 110 supplies flows to left and right motor 118 and 119 through the bottom of electro-hydraulic proportion reversing valve 122, and then through the check valve at flow divider valve 117 two ends and the next oil sump tank of electro-hydraulic proportion reversing valve 122, because road grader is in direction of retreat not operation and less demanding to roadholding, so hydraulic oil is without the shunting of flow divider valve 117.
When drive pattern select switch 124 is manually placed in the a11wheel drive pattern 125 of front-wheel assistive drive, this pattern mainly increases tractive force during road grader operation, gearbox-gear is placed in each gear of work, now the D2 electromagnet of electro-hydraulic proportion reversing valve 122 obtains electric, control D2 electromagnet current is set to maximum spool aperture position, controllable capacity pump 110 pressure oil output arrives left through electro-hydraulic proportion reversing valve 122 and flow divider valve 117, right motor 118 and 119, when front wheel drive force is greater than traction, controllable capacity pump 110 delivery pressure is less than pressure shut-off valve 112 setting pressure, now controllable capacity pump 110 is in max.cap..When front wheel drive force is less than traction, controllable capacity pump 110 delivery pressure is greater than pressure shut-off valve 112 setting pressure, pressure shut-off valve 112 action, controllable capacity pump 110 discharge capacity reduces, but because road grader trailing wheel continues to drive road grader to advance, controllable capacity pump 110 delivery pressure diminishes, pressure shut-off valve 112 action, controllable capacity pump 110 discharge capacity increases, thus maintenance front wheel rotation speed and rear wheel rotation speed match.During the situations such as load variations, straight-line travelling and steering situation, principle of work is similar to the corresponding situation of front-wheel individual drive pattern.
Claims (4)
1. a front wheel auxiliary drive system of land leveller, comprises driving engine, change speed gear box, assistive drive hydraulic efficiency pressure system and hydraulic control system, described assistive drive hydraulic efficiency pressure system comprises the integrated pressure shutoff valve (112) that oil circuit communicates, load-sensing valve (113), controllable capacity pump (110), reducing valve (115), solenoid directional control valve (116), left, right motor (118, 119), shuttle valve (121), flow regulating valve 120, described integrated pressure shutoff valve (112) is connected with driving engine by jackshaft with the controllable capacity pump (110) of load-sensing valve (113), left, right motor (118, 119) left with road grader respectively, off front wheel connects, and it is characterized in that, this hydraulic efficiency pressure system also comprises electro-hydraulic proportion reversing valve (122) and flow divider valve (117), left, right motor (118, 119) A, B mouth is directly communicated with fuel tank by the meta of flow divider valve (117) and electro-hydraulic proportion reversing valve (122), and described hydraulic control system comprises drive pattern select switch (124), front-wheel assistive drive speed adjustment knob (127), can be adjusted the control electric current of electro-hydraulic proportion reversing valve (122), realize the adjustment of front-wheel individual drive hourly velocity by front-wheel assistive drive speed adjustment knob (127).
2. front wheel auxiliary drive system of land leveller according to claim 1, it is characterized in that, drive pattern select switch (124) has back-wheel drive pattern (123), the a11wheel drive pattern (125) of front-wheel assistive drive and the Three models of front-wheel individual drive pattern (126).
3. front wheel auxiliary drive system of land leveller according to claim 2, it is characterized in that, this hydraulic efficiency pressure system also comprises electromagnetic proportion relief valve (114), and described hydraulic control system also comprises front-wheel assistive drive tractive force knob (128) driving tractive force to regulate when can realize front-wheel individual drive.
4. the front wheel auxiliary drive system of land leveller according to claim 1 or 2 or 3, is characterized in that, described left and right motor (118,119) is Double-discharge radial plunger piston motor.
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| CN201310323675.5A CN103522896B (en) | 2013-07-30 | 2013-07-30 | Front wheel auxiliary drive system of land leveller |
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| CN201310323675.5A CN103522896B (en) | 2013-07-30 | 2013-07-30 | Front wheel auxiliary drive system of land leveller |
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| CN103522896B true CN103522896B (en) | 2016-03-30 |
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| CN107725542B (en) * | 2017-11-13 | 2019-11-19 | 广西柳工机械股份有限公司 | Land leveller front wheel driven hydraulic control system |
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| CN110001390B (en) * | 2019-04-24 | 2024-02-02 | 山东临工工程机械有限公司 | Transmission system and control method |
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| CN113323930B (en) * | 2021-06-28 | 2023-05-19 | 湖南三一中型起重机械有限公司 | Multistage pressure control and pressure speed regulation hydraulic system and operation machinery |
| CN115110601B (en) * | 2022-08-30 | 2022-12-02 | 四川鼎鸿智电装备科技有限公司 | Loader system control method, unmanned loader, equipment and medium |
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