CN108442213B - Multifunctional control system of paver screed - Google Patents
Multifunctional control system of paver screed Download PDFInfo
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- CN108442213B CN108442213B CN201810418467.6A CN201810418467A CN108442213B CN 108442213 B CN108442213 B CN 108442213B CN 201810418467 A CN201810418467 A CN 201810418467A CN 108442213 B CN108442213 B CN 108442213B
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- 238000006073 displacement reaction Methods 0.000 claims description 48
- 238000000034 method Methods 0.000 claims description 14
- 238000001514 detection method Methods 0.000 claims description 6
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 230000008859 change Effects 0.000 claims description 3
- 230000001934 delay Effects 0.000 claims description 3
- 238000005259 measurement Methods 0.000 claims description 3
- 238000007373 indentation Methods 0.000 abstract description 5
- 230000009194 climbing Effects 0.000 abstract description 4
- 230000002265 prevention Effects 0.000 abstract description 4
- 230000008569 process Effects 0.000 description 8
- 230000009471 action Effects 0.000 description 5
- 238000010276 construction Methods 0.000 description 5
- 230000005484 gravity Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 230000001174 ascending effect Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000011384 asphalt concrete Substances 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 239000010410 layer Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 239000002344 surface layer Substances 0.000 description 1
Classifications
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
- E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
- E01C19/12—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for distributing granular or liquid materials
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Road Paving Machines (AREA)
Abstract
The utility model discloses a multifunctional control system of a paver screed, which comprises a two-position four-way electromagnetic reversing valve I, a three-position four-way electromagnetic reversing valve I, a one-way throttle valve, a reversing pressure reducing valve I, a reversing pressure reducing valve II, a two-position four-way electromagnetic reversing valve II, a hydraulic valve block, a first electromagnetic valve and a second electromagnetic valve which are arranged in rod cavities of left and right lifting cylinders. The control system of the utility model not only can realize the functions of lifting, descending, floating, locking, assisting, climbing prevention and the like of the screed of the paver; in addition, on the control of the assistance function of the screed, the simultaneous assistance of the lifting cylinders on the left side and the right side can be realized according to the needs, or the independent assistance control can be realized, and the problems of road surface bulge or indentation and the like can be effectively solved.
Description
Technical Field
The utility model relates to a paver control system, in particular to a multifunctional control system of a screed plate of a paver.
Background
In road construction maintenance construction, the paver is used as one of important construction equipment and is mainly applied to paving of stabilized soil materials or asphalt concrete materials of a high-grade highway base layer and a surface layer. The screed is used as a main working device of the paver, and the control of the functions of the screed plays a vital role in the paving quality of the pavement in the whole paving operation process. According to the construction requirements of paving operation, the control of the screed is generally realized through a lifting cylinder hydraulic system, and the functions of lifting, descending, floating, locking, assisting and the like are included. Most of the current control on the screed plate functions only pursues the realization of the individual functions and requires additional hydraulic circuits for control, which not only causes the hydraulic circuits to be complex but also cannot meet the requirements of special construction operations. If the power assisting function is realized, the lifting oil cylinders on the left side and the right side can only realize the simultaneous power assisting, and the power assisting control cannot be independently performed, so that the paving operation of the road surface with the transverse gradient cannot be realized.
The paving operation process of the paver generally comprises three stages of stopping, starting and paving, wherein in the stopping and starting processes of the paver, the stress state of the screed plate can be changed, and if the control treatment of the screed plate is improper at the moment, pavement defects such as bulges or indentations on the pavement can be caused. In order to solve the problem, most of the screed plates at present lock the lifting cylinder during the stopping and starting processes of the paver so as to avoid the screed plate from displacing. However, when the lifting oil cylinder is locked for a short time, the suction phenomenon of the upper cavity of the lifting oil cylinder can generate negative pressure, and then the screed plate can upwards generate displacement under the action of the supporting force of the bottom surface material, so that the pavement bulge is caused, and the pavement quality is influenced.
The Chinese patent application No. 2014108247568 discloses a hydraulic control device for a screed of a paver, which can realize the functions of lifting, lowering, floating and locking of the screed, although avoiding the potential safety hazard caused by too fast lowering of the screed due to misoperation, in 2014, 12 and 27. However, the complete floating of the screed plate in the paving process cannot be realized due to the influence of the throttle valve, the pavement paving quality is influenced, and the booster function of the screed plate cannot be realized. As before, the problems of bulge or indentation and the like generated in the stopping and starting stages of the paver can not be fundamentally solved.
The Chinese patent application No. 2015206998581 discloses a hydraulic control system and a paver on the 9 th month 11 th year 2015, wherein the hydraulic control system can also realize the functions of lifting, descending, floating, locking, assisting and the like of a screed plate although avoiding the phenomenon of sucking air generated by an upper cavity of a lifting cylinder in the locking process. However, in the floating process of the screed, the screed still cannot enter a completely floating state due to the back pressure of the upper cavity and the lower cavity of the lifting oil cylinder, and in the control of the assistance function, the simultaneous assistance of the lifting oil cylinders on the left side and the right side can be realized only, and the assistance control cannot be independently performed.
Disclosure of Invention
Aiming at the defects in the prior art, the utility model provides a multifunctional control system of a screed of a paver, which can realize the functions of lifting, descending, floating, locking, assisting, climbing prevention and the like of the screed of the paver; furthermore, in the control of the assistance function of the screed, the simultaneous assistance of the lifting cylinders on the left side and the right side can be realized or independent assistance control can be realized according to the needs; furthermore, a control method for the screed plate of the paver in the stopping and starting stages is provided, and the problems of road bulge or indentation and the like can be effectively solved.
In order to achieve the above purpose, the technical scheme adopted by the utility model is as follows: the multifunctional control system of the paver screed plate comprises a hydraulic control system;
the hydraulic control system comprises a first two-position four-way electromagnetic reversing valve, a first three-position four-way electromagnetic reversing valve, a one-way throttle valve, a first reversing pressure reducing valve, a second two-position four-way electromagnetic reversing valve, a hydraulic valve block, and a first electromagnetic valve and a second electromagnetic valve which are respectively arranged on a rod cavity of the left lifting oil cylinder and a rod cavity of the right lifting oil cylinder. The hydraulic valve block comprises a main oil way, an oil return way and a flow valve, wherein the flow valve divides the main oil way into two pressure oil ways Pc and Pd and is respectively connected with pressure measuring interfaces M2 and M3 of the hydraulic valve block.
The high-pressure port P1 and the oil return port T1 of the two-position four-way electromagnetic reversing valve I are respectively connected with the main oil path Pa and the first oil return path Ta of the hydraulic valve block, and the two control ports A1 and B1 are respectively connected with the second oil return path Tb and the pressure measuring port M1 of the hydraulic valve block;
the high-pressure port P2 and the oil return port T2 of the first three-position four-way electromagnetic reversing valve are respectively connected with a pressure oil way Pe of the flow valve and a third oil return way Tc of the hydraulic valve block, and the two control ports A2 and B2 are respectively connected with a first oil outlet Aa and a second oil outlet Ba of the hydraulic valve block; the one-way throttle valve is connected in series between a control port B2 of the first three-position four-way electromagnetic reversing valve and a second oil outlet Ba oil way of the hydraulic valve block;
the reversing pressure reducing valve I comprises a three-position four-way electromagnetic reversing valve II and a pressure reducing one-way valve I, a high pressure port P3 and an oil return port T3 of the three-position four-way electromagnetic reversing valve II are respectively connected with another pressure oil way Pf of the flow valve and a fourth oil return way Td of the hydraulic valve block, one control port A3 and the pressure reducing one-way valve I are connected in series and then connected with an outlet Ac of the one-way throttle valve, and the other control port B3 is plugged on the hydraulic valve block;
the reversing and reducing valve II comprises a three-position four-way electromagnetic reversing valve III and a reducing one-way valve II, wherein a high-pressure port P4 and an oil return port T4 of the three-position four-way electromagnetic reversing valve III are respectively connected with another pressure oil way Ps of the flow valve and a fifth oil return way Te of the hydraulic valve block, and a control port A4 and the reducing one-way valve II are connected in series and then connected with an oil return port T5 of the two-position four-way electromagnetic reversing valve II; the other control port B4 is plugged on the hydraulic valve block;
the high-pressure port P5 of the two-position four-way electromagnetic reversing valve II is connected with the outlet Ac of the one-way throttle valve, one control port A5 is connected with the third oil outlet Ab of the hydraulic valve block, and the other control port B5 is plugged on the hydraulic valve block;
the hydraulic valve block further comprises a first overflow valve, a third electromagnetic valve, a fourth electromagnetic valve, a second overflow valve and a third overflow valve, and the overflow valves are connected in parallel between a pressure oil way Pd of the flow valve and a fourth oil return way Td of the hydraulic valve block; the overflow valve II is connected in parallel between a control port A2 of the three-position four-way electromagnetic reversing valve I and a third oil return channel Tc of the hydraulic valve block; the overflow valve III is connected in parallel between a control port B1 of the two-position four-way electromagnetic reversing valve I and a first oil return path Ta of the hydraulic valve block; the electromagnetic valve III is connected in parallel between the outlet of the one-way throttle valve and the control port A2 of the three-position four-way electromagnetic reversing valve I; the electromagnetic valve IV is connected in series between the inlet of the overflow valve II and the first oil outlet Aa of the hydraulic valve block;
the first oil outlet Aa of the hydraulic valve block is connected with rodless cavities of the left lifting oil cylinder and the right lifting oil cylinder respectively;
the second oil outlet Ba of the hydraulic valve block is connected with the second electromagnetic valve in series and then is connected with a rod cavity of the right lifting oil cylinder;
and the third oil outlet Ab of the hydraulic valve block is connected with the first electromagnetic valve in series and then is connected with a rod cavity of the left lifting oil cylinder.
The hydraulic control system also comprises a left lifting oil cylinder pressure sensor and a right lifting oil cylinder pressure sensor;
the left lifting oil cylinder pressure sensor is arranged on a rod cavity of the left lifting oil cylinder;
the right lifting oil cylinder pressure sensor is arranged on a rod cavity of the right lifting oil cylinder;
the device also comprises a left lifting oil cylinder displacement sensor and a right lifting oil cylinder displacement sensor;
the left lifting oil cylinder displacement sensor is arranged on a piston rod of the left lifting oil cylinder;
the right lifting cylinder displacement sensor is arranged on a piston rod of the right lifting cylinder.
Preferably, the middle position function of the two-position four-way electromagnetic reversing valve I and the two-position four-way electromagnetic reversing valve II is II type;
preferably, the middle position function of the first three-position four-way electromagnetic reversing valve is K-type;
preferably, the middle position function of the three-position four-way electromagnetic reversing valve II and the three-position four-way electromagnetic reversing valve III is Y-shaped;
preferentially, the pressure regulation of the first reversing pressure reducing valve and the second reversing pressure reducing valve is electric proportional regulation;
the hydraulic control system comprises an operating platform, a controller, a left lifting oil cylinder pressure sensor, a right lifting oil cylinder pressure sensor, a left lifting oil cylinder displacement sensor and a right lifting oil cylinder displacement sensor, wherein the left lifting oil cylinder pressure sensor, the right lifting oil cylinder pressure sensor, the left lifting oil cylinder displacement sensor and the right lifting oil cylinder displacement sensor are connected with the input end of the controller; the electric control system also comprises interfaces of corresponding electromagnetic valves in the hydraulic control system connected with the output end of the controller, wherein the interfaces comprise a first interface of a two-position four-way electromagnetic reversing valve, a first interface of a three-position four-way electromagnetic reversing valve, a second interface of the three-position four-way electromagnetic reversing valve, a third interface of the three-position four-way electromagnetic reversing valve, a second interface of the two-position four-way electromagnetic reversing valve, a first interface of the electromagnetic valve, a second interface of the electromagnetic valve, a third interface of the electromagnetic valve and a fourth interface of the electromagnetic valve;
the utility model also provides a control method of the paver to the screed plate in the stopping and starting stages, which comprises the following steps:
1) The operator triggers a parking instruction through the console, and the controller immediately sends out an anti-climbing function instruction to the hydraulic control system to control the anti-climbing function of the screed plate;
2) The left lifting oil cylinder displacement sensor and the right lifting oil cylinder displacement sensor monitor the displacement of the screed plate in real time, and when the displacement detection value is larger than the measured value of the paving thickness before stopping, the controller sends a locking function instruction to the hydraulic control system to control the locking function of the screed plate; otherwise, continuing to control the anti-climbing function of the screed plate;
3) After stopping, until an operator triggers a starting instruction through an operating board, a controller delays for a set time and then sends a floating function instruction to a hydraulic control system to control a floating function of the screed;
4) The left lifting cylinder displacement sensor and the right lifting cylinder displacement sensor monitor the displacement of the screed plate in real time, when the displacement detection value is smaller than the paving thickness measurement value before stopping, the controller sends a power-assisting function instruction to the hydraulic control system to control the power-assisting function of the screed plate, the controller can detect the power-assisting pressure of the screed plate according to the left lifting cylinder pressure sensor and the right lifting cylinder pressure sensor, the power-assisting pressure is regulated in real time through the hydraulic control system along with the change of the left lifting cylinder displacement and the right lifting cylinder displacement, the influence of the gravity of the screed plate is reduced, and the screed plate is enabled to quickly enter a floating state; otherwise, continuing to control the floating function of the screed.
Compared with the prior art, the utility model has the advantages and positive effects that:
the multifunctional control system of the paver screed plate not only can realize the functions of lifting, descending, floating, locking, assisting, climbing prevention and the like of the paver screed plate; in addition, on the control of the boosting function of the screed, the lifting cylinders on the left side and the right side can be boosted simultaneously or independently according to the requirement; and on the basis, a control method of the paver on the screed plate in the stopping and starting stages is provided, so that the problems of road bulge or indentation and the like can be effectively solved.
Drawings
Fig. 1: is a schematic diagram of the hydraulic control system of the present utility model;
in the figure: 1. a two-position four-way electromagnetic reversing valve I, a 2-position four-way electromagnetic reversing valve I, a 3-position one-way throttle valve,
4. a reversing pressure reducing valve I, a 4.1 three-position four-way electromagnetic reversing valve II, a 4.2 pressure reducing one-way valve I,
5. a reversing pressure reducing valve II, a 5.1 three-position four-way electromagnetic reversing valve III, a 5.2 pressure reducing one-way valve II,
6. two-position four-way electromagnetic reversing valves II, 7, a hydraulic valve block, 7.1, an overflow valve I, 7.2 and an electromagnetic valve III,
7.3, a fourth electromagnetic valve, 7.4, a second overflow valve, 7.5, a flow valve, 7.6 and a third overflow valve,
8. left lift cylinder, 8.1, left lift cylinder pressure sensor, 8.2, left lift cylinder displacement sensor, 9, right lift cylinder, 9.1, right lift cylinder pressure sensor, 9.2, right lift cylinder displacement sensor, 10, solenoid valve one, 11, solenoid valve two,
fig. 2: is a structural block diagram of the electrical control system of the present utility model;
fig. 3: the utility model relates to a control method flow chart of a paver on a screed plate in the stopping and starting stages.
Detailed Description
In order to better understand the aspects of the present utility model, the present utility model will be described in further detail with reference to the accompanying drawings and detailed description.
The multifunctional control system of the paver screed plate comprises a hydraulic control system and an electric control system;
the hydraulic control system shown in fig. 1 comprises a two-position four-way electromagnetic directional valve 1, a three-position four-way electromagnetic directional valve 2, a one-way throttle valve 3, a directional pressure reducing valve 4, a directional pressure reducing valve 5, a two-position four-way electromagnetic directional valve 6, a hydraulic valve block 7, a solenoid valve 10 with a rod cavity and a solenoid valve 11 with a rod cavity and arranged on a left lifting oil cylinder 8 and a right lifting oil cylinder 9. The hydraulic valve block 7 comprises a main oil path P, an oil return path T and a flow valve 7.5, wherein the flow valve 7.5 divides the main oil path P into two pressure oil paths Pc and Pd and is respectively connected with pressure measuring interfaces M2 and M3 of the hydraulic valve block 7.
The high-pressure port P1 and the oil return port T1 of the two-position four-way electromagnetic reversing valve I1 are respectively connected with the main oil path Pa and the oil return path Ta of the hydraulic valve block 7, and the two control ports A1 and B1 are respectively connected with the oil return path Tb and the pressure measuring port M1 of the hydraulic valve block 7;
the high-pressure port P2 and the oil return port T2 of the three-position four-way electromagnetic reversing valve I2 are respectively connected with a pressure oil way Pe of the flow valve 7.5 and an oil return way Tc of the hydraulic valve block 7, and the two control ports A2 and B2 are respectively connected with an oil outlet Aa and an oil outlet Ba of the hydraulic valve block 7; the one-way throttle valve 3 is connected in series between a control port B2 of the three-position four-way electromagnetic reversing valve I2 and an oil outlet Ba oil way of the hydraulic valve block 7;
the reversing and reducing valve I4 comprises a three-position four-way electromagnetic reversing valve II 4.1 and a reducing one-way valve I4.2, a high-pressure port P3 and an oil return port T3 of the three-position four-way electromagnetic reversing valve II 4.1 are respectively connected with another pressure oil way Pf of the flow valve 7.5 and an oil return way Td of the hydraulic valve block 7, one control port A3 and the reducing one-way valve I4.2 are connected in series and then are connected with an outlet Ac of the one-way throttle valve 3, and the other control port B3 is plugged on the hydraulic valve block 7;
the reversing and reducing valve II 5 comprises a three-position four-way electromagnetic reversing valve III 5.1 and a reducing one-way valve II 5.2, a high-pressure port P4 and an oil return port T4 of the three-position four-way electromagnetic reversing valve III 5.1 are respectively connected with another pressure oil way Ps of the flow valve 7.5 and an oil return way Te of the hydraulic valve block 7, and a control port A4 and the reducing one-way valve II 5.2 are connected in series and then are connected with an oil return port T5 of the two-position four-way electromagnetic reversing valve II 6; the other control port B4 is plugged on the hydraulic valve block 7;
the high-pressure port P5 of the two-position four-way electromagnetic reversing valve II 6 is connected with the outlet Ac of the one-way throttle valve 3, one control port A5 is connected with the oil outlet Ab of the hydraulic valve block 7, and the other control port B5 is plugged on the hydraulic valve block 7;
the hydraulic valve block 7 further comprises a first overflow valve 7.1, a third electromagnetic valve 7.2, a fourth electromagnetic valve 7.3, a second overflow valve 7.4 and a third overflow valve 7.6, wherein the first overflow valve 7.1 is connected in parallel between a pressure oil path Pd of the flow valve 7.5 and an oil return path Td of the hydraulic valve block 7; the overflow valve II 7.4 is connected in parallel between a control port A2 of the three-position four-way electromagnetic reversing valve I2 and an oil return channel Tc of the hydraulic valve block 7; the overflow valve III 7.6 is connected in parallel between a control port B1 of the two-position four-way electromagnetic reversing valve I1 and an oil return path Ta of the hydraulic valve block 7; the electromagnetic valve III 7.2 is connected in parallel between the outlet of the unidirectional throttle valve 3 and the control port A2 of the three-position four-way electromagnetic reversing valve I2; the electromagnetic valve IV 7.3 is connected in series between the inlet of the overflow valve II 7.4 and the oil outlet Aa of the hydraulic valve block 7;
the oil outlets Aa of the hydraulic valve blocks 7 are respectively connected with rodless cavities of the left lifting oil cylinder 8 and the right lifting oil cylinder 9;
the oil outlet Ba of the hydraulic valve block 7 is connected with the second electromagnetic valve 11 in series and then is connected with a rod cavity of the right lifting oil cylinder 9;
an oil outlet Ab of the hydraulic valve block 7 is connected with a first electromagnetic valve 10 in series and then is connected with a rod cavity of the left lifting oil cylinder 8;
preferably, the middle position function of the two-position four-way electromagnetic reversing valve 1 is II type, and when the two-position four-way electromagnetic reversing valve is not electrified, a main oil way P in a hydraulic system can be communicated with an oil return way T to unload the pressure of the system; the middle position function of the two-position four-way electromagnetic reversing valve II is also II type, and when the power is not on, the left lifting oil cylinder 8 and the rod cavity oil way of the right lifting oil cylinder 9 can be communicated;
preferably, the middle position function of the three-position four-way electromagnetic directional valve I2 is K-shaped, and when the three-position four-way electromagnetic directional valve I is not electrified, the rodless cavity oil ways of the left lifting oil cylinder 8 and the right lifting oil cylinder 9 can be simultaneously communicated with the oil return way T of the hydraulic valve block 7;
preferably, the median functions of the three-position four-way electromagnetic directional valve II 4.1 and the three-position four-way electromagnetic directional valve III 5.1 are Y-shaped, and when the three-position four-way electromagnetic directional valve II 4.1 and the three-position four-way electromagnetic directional valve III 5.1 are not electrified, two control ports of the three-position four-way electromagnetic directional valve II and the three-position four-way electromagnetic directional valve III 5.1 are communicated with an oil return path T of the hydraulic valve block 7, so that the reversing pressure reducing valve I4 and the reversing pressure reducing valve II 5 do not work;
the pressure adjustment of the reversing pressure reducing valve I4 and the reversing pressure reducing valve II 5 is electric proportional adjustment, and can be used for adjusting the booster pressure of a rod cavity of the left lifting oil cylinder 8 and the booster pressure of a rodless cavity of the right lifting oil cylinder 9;
the electric control system shown in fig. 2 comprises an operation console, a controller, a left lifting oil cylinder pressure sensor, a right lifting oil cylinder pressure sensor, a left lifting oil cylinder displacement sensor and a right lifting oil cylinder displacement sensor which are connected with the input end of the controller; the interface of the corresponding electromagnetic valve in the hydraulic control system connected with the output end of the controller is provided with an interface Y1.1 of a two-position four-way electromagnetic reversing valve I1, interfaces Y2.1 and Y3.1 of a three-position four-way electromagnetic reversing valve I2, an interface Y4.1 of a three-position four-way electromagnetic reversing valve II 4.1, an interface Y5.1 of a three-position four-way electromagnetic reversing valve III 5.1, an interface Y6.1 of a two-position four-way electromagnetic reversing valve II 6, an interface Y9.1 of an electromagnetic valve I10, an interface Y10.1 of an electromagnetic valve II 11, an interface Y7.2.1 of an electromagnetic valve III 7.2 and an interface Y7.3.1 of an electromagnetic valve IV 7.3;
the left lifting cylinder pressure sensor 8.1 is arranged in a rod cavity of the left lifting cylinder 8, and the right lifting cylinder pressure sensor 9.1 is arranged in a rod cavity of the right lifting cylinder 9; the left lifting cylinder displacement sensor 8.2 is arranged on a piston rod of the left lifting cylinder 8, and the right lifting cylinder displacement sensor 9.2 is arranged on a piston rod of the right lifting cylinder 9;
the multifunctional control system of the screed of the paver of the utility model can realize the following functional control of the screed of the paver, and is described in detail with reference to fig. 1:
when the paver screed plate implements the ascending function, the electromagnet Y1 of the two-position four-way electromagnetic reversing valve 1, the electromagnet Y2 of the three-position four-way electromagnetic reversing valve 2 and the electromagnet Y7 of the electromagnetic valve four 7.2 are powered off, and the rest electromagnets Y3, Y4, Y5, Y6, Y8, Y9 and Y10 are powered off, at the moment, a main oil way P of the hydraulic valve block 7 flows through a high-pressure port P2 and a control port B2 of the three-position four-way electromagnetic reversing valve 1 from Pb, pc and Pe ports, then flows through a one-way valve channel of the one-way throttle valve 3 to divide two ways, one way of the two-way valve channel flows through a high-pressure port P5 and a control port A5 of the two-position four-way electromagnetic reversing valve 2, and flows out of an outlet of the hydraulic valve block 7 to be conducted to a rod cavity Ab of the left lifting cylinder 8 from the electromagnetic valve 10 arranged on the rod cavity of the left lifting cylinder 8; the other path flows out from the oil outlet Ba of the hydraulic valve block 7, and conducts the electromagnetic valve II 11 arranged on the rod cavity of the right lifting oil cylinder 9 to the rod cavity of the right lifting oil cylinder 9, so that the left lifting oil cylinder 8 and the right lifting oil cylinder 9 are lifted. The pressure of the system is now defined by the relief valve three 7.6 and can be measured via the pressure tap M1 in the hydraulic valve block 7.
When the paver screed plate implements the descending function, the electromagnet Y1 of the two-position four-way electromagnetic reversing valve 1, the electromagnet Y3 of the three-position four-way electromagnetic reversing valve 2, the electromagnet Y7 of the electromagnetic valve four 7.2, the electromagnet Y9 of the electromagnetic valve 10 and the electromagnet Y10 of the electromagnetic valve two 11 are powered off, and the rest electromagnets Y2, Y4, Y5, Y6 and Y8 are powered off, so that a main oil path P of the hydraulic valve block 7 flows through a high-pressure port P2 and a control port A2 of the three-position four-way electromagnetic reversing valve one 2 from the ports Pb, pc and Pe and flows out from an oil outlet Aa of the hydraulic valve block 7 to enter rodless cavities of the left lifting oil cylinder 8 and the right lifting oil cylinder 9 through the electromagnetic valve four 7.3, and the left lifting oil cylinder and the right lifting oil cylinder are descended; the oil with the rod cavity of the left lifting oil cylinder 8 flows to the one-way throttle valve 3 through the first electromagnetic valve 10, the oil outlet Ab of the hydraulic valve block 7 and the control port A5 and the high-pressure port P5 of the two-position four-way electromagnetic reversing valve 2, and the oil with the rod cavity of the right lifting oil cylinder 9 also flows to the one-way throttle valve 3 through the second electromagnetic valve 11 and the oil outlet Ba of the hydraulic valve block 7, and at the moment, the oil with the rod cavities of the left lifting oil cylinder 8 and the right lifting oil cylinder 9 flows through the throttle channel of the one-way throttle valve 3 together and returns to the oil return channel T of the hydraulic valve block 7 through the control port B2 and the oil return port T2 of the three-position four-way electromagnetic reversing valve 2. At this time, the descending pressure of the lifting cylinder is limited by the overflow valve II 7.4, and the screed of the paver can be stably descended under the action of the throttling channel of the unidirectional throttling valve 3.
When the paver screed plate implements the floating function, only the electromagnet Y9 of the first electromagnetic valve 10 and the electromagnet Y10 of the second electromagnetic valve 11 are required to be powered on, and the rest electromagnets Y1, Y2, Y3, Y4, Y5, Y6, Y7 and Y8 are powered off, so that oil in the upper cavity and the lower cavity of the left lifting oil cylinder 8 and the right lifting oil cylinder 9 of the screed plate are simultaneously communicated with an oil return path T of the hydraulic valve block 7 through the third electromagnetic valve 7.2 and the K-shaped middle position of the third-position four-way electromagnetic reversing valve 2, and the floating of the screed plate is realized. The upper cavity and the lower cavity of the lifting oil cylinder are not affected by any damping in the oil flowing process, so that the complete floating of the screed plate of the paver can be realized.
When the paver screed plate implements the locking function, only the electromagnet Y8 of the electromagnetic valve IV 7.3 is electrified, and the rest electromagnets Y1, Y2, Y3, Y4, Y5, Y6, Y7, Y9 and Y10 are all powered off, so that the oil in the upper cavity and the lower cavity of the left lifting oil cylinder 8 and the right lifting oil cylinder 9 of the paver screed plate are locked by the electromagnetic valve 7.3, the electromagnetic valve I10 and the electromagnetic valve II 11, and the lifting oil cylinders cannot act.
When the paver screed plate implements the power assisting function, the technical scheme has the advantage that the lifting cylinders on the left side and the right side can be simultaneously assisted or independently assisted for control as required. When the lifting cylinders on the left side and the right side are needed to assist power simultaneously, the electromagnet Y1 of the two-position four-way electromagnetic reversing valve I1, the electromagnet Y4 of the three-position four-way electromagnetic reversing valve II 4.1, the electromagnet Y7 of the electromagnetic valve IV 7.2, the electromagnet Y9 of the electromagnetic valve I10 and the electromagnet Y10 of the electromagnetic valve II 11 are powered on, and the rest electromagnets Y2, Y3, Y5, Y6 and Y8 are powered off, at the moment, a main oil way P of the hydraulic valve block 7 flows through a high-pressure port P3 and a control port A3 of the flow valve 7.5 and a port Pd of the three-position four-way electromagnetic reversing valve II 4.1, is depressurized to a decompression one-way valve I4.2, and then is divided into two paths after the inlet pressure is depressurized, one path flows through a high-pressure port P5 and a control port A5 of the two-position four-way electromagnetic reversing valve II 6, flows out of an oil outlet Ab of the hydraulic valve block 7 and flows into a rod cavity of the left lifting cylinder 8 through the electromagnetic valve I10 arranged on the rod cavity of the left lifting cylinder 8; the other path flows out from the oil outlet Ba of the hydraulic valve block 7 and passes through a second electromagnetic valve 11 arranged on the rod cavity of the right lifting oil cylinder 9 to the rod cavity of the right lifting oil cylinder 9. At the moment, the boosting pressure of the screed plate of the paver is regulated by the decompression one-way valve II 4.2, so that the rod cavity of the lifting oil cylinder always maintains certain back pressure, and the action of the gravity of the screed plate on the paving mixture is lightened. The back pressure of the lift cylinder rod cavity can be monitored by a left lift cylinder pressure sensor 8.1 installed on the rod cavity of the left lift cylinder 8 and a right lift cylinder pressure sensor 9.1 installed on the rod cavity of the right lift cylinder 9 in the electrical control system. When the lifting cylinders on the left side and the right side are required to independently assist, the following operation is required to be performed on the basis of simultaneous assistance of the lifting cylinders on the left side and the right side, namely, the electromagnet Y5 of the three-position four-way electromagnetic reversing valve three 5.1 and the electromagnet Y6 of the two-position four-way electromagnetic reversing valve two 6 are powered on, so that the assistance adjustment of the rod cavity of the left lifting cylinder 8 by the reversing pressure reducing valve one 4 can be realized, and the assistance adjustment of the rod cavity of the right lifting cylinder 9 by the reversing pressure reducing valve 5 can be realized.
When the paver screed plate implements the climbing prevention function, the electromagnet Y1 of the two-position four-way electromagnetic directional valve 1, the electromagnet Y3 of the three-position four-way electromagnetic directional valve 2 and the electromagnet Y7 of the electromagnetic valve four 7.2 are electrified, and the rest electromagnets Y2, Y4, Y5, Y6, Y8, Y9 and Y10 are all powered off, at the moment, the main oil path P of the hydraulic valve block 7 flows through the high-pressure port P2 and the control port A2 of the three-position four-way electromagnetic directional valve one 2 from the Pb, pc and Pe ports of the flow valve, and flows out from the oil outlet Aa of the hydraulic valve block 7 through the electromagnetic valve four 7.3 to enter rodless cavities of the left lifting oil cylinder 8 and the right lifting oil cylinder 8 and 9, and the rodless cavity of the right lifting oil cylinder 9 cannot descend under the action of the electromagnetic valve one 10, so that the rodless cavity of the right lifting oil cylinder 9 cannot descend under the action of the electromagnetic valve two 11, and the rodless cavity of the left lifting oil cylinder and right lifting cylinder can keep a certain pressure, and the screed plate is prevented from ascending for a short time. The back pressure of the rodless cavity of the lifting oil cylinder can be adjusted through the overflow valve II 7.4.
The utility model also provides a control method for the screed plate of the paver in the stopping and starting stages, which is shown in the figure 3, and comprises the following steps:
1) The operator triggers a parking instruction through an operation console in the electric control system, and the controller immediately sends out an anti-climbing function instruction to the hydraulic control system to control the anti-climbing function of the screed plate;
2) The left lifting oil cylinder displacement sensor and the right lifting oil cylinder displacement sensor monitor the displacement of the screed plate in real time, and when the displacement detection value is larger than the measured value of the paving thickness before stopping, the controller sends a locking function instruction to the hydraulic control system to control the locking function of the screed plate; otherwise, continuing to control the anti-climbing function of the screed plate;
3) After stopping, until an operator triggers a starting instruction through an operating console in the electric control system, the controller delays for 5 seconds and then sends a floating function instruction to the hydraulic control system to control the floating function of the screed;
4) The left lifting cylinder displacement sensor and the right lifting cylinder displacement sensor monitor the displacement of the screed plate in real time, when the displacement detection value is smaller than the paving thickness measurement value before stopping, the controller sends a power-assisting function instruction to the hydraulic control system to control the power-assisting function of the screed plate, the controller can detect the power-assisting pressure of the screed plate according to the left lifting cylinder pressure sensor and the right lifting cylinder pressure sensor, the power-assisting pressure is regulated in real time through the hydraulic control system along with the change of the left lifting cylinder displacement and the right lifting cylinder displacement, the influence of the gravity of the screed plate is reduced, and the screed plate is enabled to quickly enter a floating state; otherwise, continuing to control the floating function of the screed.
Of course, the above embodiments are merely preferred embodiments of the present utility model, and are not limited thereto, and on the basis of these, specific adjustments may be made according to actual needs, thereby obtaining different embodiments. All equivalent changes or modifications made in accordance with the scope of the present utility model are intended to fall within the scope of the present utility model.
Claims (8)
1. The multifunctional control system of the paver screed is characterized by comprising a two-position four-way electromagnetic reversing valve I (1), a three-position four-way electromagnetic reversing valve I (2), a one-way throttle valve (3), a reversing pressure reducing valve I (4), a reversing pressure reducing valve II (5), a two-position four-way electromagnetic reversing valve II (6), a hydraulic valve block (7), and an electromagnetic valve I (10) and an electromagnetic valve II (11) which are respectively arranged on a rod cavity of a left lifting oil cylinder (8) and a rod cavity of a right lifting oil cylinder (9); the hydraulic valve block (7) comprises a first overflow valve (7.1), a third electromagnetic valve (7.2), a fourth electromagnetic valve (7.3), a second overflow valve (7.4), a flow valve (7.5) and a third overflow valve (7.6);
the high-pressure port P1 and the oil return port T1 of the two-position four-way electromagnetic reversing valve I (1) are respectively connected with the main oil path Pa and the first oil return path Ta of the hydraulic valve block 7, and the two control ports A1 and B1 are respectively connected with the second oil return path Tb and the pressure measuring interface M1 of the hydraulic valve block (7);
the high-pressure port P2 and the oil return port T2 of the three-position four-way electromagnetic reversing valve I (2) are respectively connected with a pressure oil way Pe of the flow valve (7.5) and a third oil return way Tc of the hydraulic valve block (7), and the two control ports A2 and B2 are respectively connected with a first oil outlet Aa and a second oil outlet Ba of the hydraulic valve block (7); the one-way throttle valve (3) is connected in series between a control port B2 of the three-position four-way electromagnetic reversing valve I (2) and a second oil outlet Ba of the hydraulic valve block (7);
the reversing and reducing valve I (4) comprises a three-position four-way electromagnetic reversing valve II (4.1) and a reducing one-way valve I (4.2), a high-pressure port P3 and an oil return port T3 of the three-position four-way electromagnetic reversing valve II (4.1) are respectively connected with another pressure oil way Pf of the flow valve (7.5) and a fourth oil return way Td of the hydraulic valve block (7), one control port A3 and the reducing one-way valve I (4.2) are connected in series and then are connected with an outlet Ac of the one-way throttle valve (3), and the other control port B3 is plugged on the hydraulic valve block (7);
the reversing and pressure reducing valve II (5) comprises a three-position four-way electromagnetic reversing valve III (5.1) and a pressure reducing one-way valve II (5.2), a high-pressure port P4 and an oil return port T4 of the three-position four-way electromagnetic reversing valve III (5.1) are respectively connected with another pressure oil way Ps of the flow valve (7.5) and a fifth oil return way Te of the hydraulic valve block 7, and a control port A4 and the pressure reducing one-way valve II (5.2) are connected in series and then are connected with an oil return port T5 of the two-position four-way electromagnetic reversing valve II (6); the other control port B4 is plugged on the hydraulic valve block (7);
the high-pressure port P5 of the two-position four-way electromagnetic reversing valve II (6) is connected with the outlet Ac of the one-way throttle valve (3), one control port A5 is connected with the third oil outlet Ab of the hydraulic valve block (7), and the other control port B5 is plugged on the hydraulic valve block (7);
the flow valve (7.5) divides the main oil path P into two pressure oil paths Pc and Pd and is respectively connected with two pressure measuring interfaces M2 and M3 of the hydraulic valve block (7), and the overflow valve I (7.1) is connected in parallel between one pressure oil path Pd of the flow valve (7.5) and a fourth oil return path Td of the hydraulic valve block (7); the overflow valve II (7.4) is connected in parallel between a control port A2 of the three-position four-way electromagnetic reversing valve I (2) and a third oil return channel Tc of the hydraulic valve block (7); the overflow valve III (7.6) is connected in parallel between a control port B1 of the two-position four-way electromagnetic reversing valve I (1) and a first oil return path Ta of the hydraulic valve block (7); the electromagnetic valve III (7.2) is connected in parallel between the outlet of the one-way throttle valve (3) and the control port A2 of the three-position four-way electromagnetic reversing valve I (2); the electromagnetic valve IV (7.3) is connected in series between the inlet of the overflow valve II (7.4) and the first oil outlet Aa of the hydraulic valve block (7);
the first oil outlet Aa of the hydraulic valve block (7) is connected with rodless cavities of the left lifting oil cylinder (8) and the right lifting oil cylinder (9) respectively;
the second oil outlet Ba of the hydraulic valve block (7) is connected with the second electromagnetic valve (11) in series and then is connected with a rod cavity of the right lifting oil cylinder (9);
the third oil outlet Ab of the hydraulic valve block (7) is connected with the first electromagnetic valve (10) in series and then is connected with a rod cavity of the left lifting oil cylinder (8).
2. The multi-function control system of a screed of a paving machine of claim 1, further comprising a left lift cylinder pressure sensor and a right lift cylinder pressure sensor;
the left lifting oil cylinder pressure sensor is arranged on a rod cavity of the left lifting oil cylinder;
the right lift cylinder pressure sensor is mounted on the rod cavity of the right lift cylinder.
3. The multi-function control system of a screed of a paving machine of claim 1, further comprising a left lift cylinder displacement sensor and a right lift cylinder displacement sensor;
the left lifting oil cylinder displacement sensor is arranged on a piston rod of the left lifting oil cylinder;
the right lifting cylinder displacement sensor is arranged on a piston rod of the right lifting cylinder.
4. The multifunctional control system of the screed of the paver according to claim 1, wherein the median functions of the two-position four-way electromagnetic directional valve one (1) and the two-position four-way electromagnetic directional valve two (6) are of type II.
5. The multifunctional control system of a screed of a paver according to claim 1, wherein the median function of the three-position four-way electromagnetic directional valve one (2) is of the K-type.
6. The multifunctional control system of the screed of the paver according to claim 1, wherein the median functions of the three-position four-way electromagnetic directional valve two (4.1) and the three-position four-way electromagnetic directional valve three (5.1) are of the Y type.
7. The multifunctional control system of a screed of a paver according to claim 1, wherein the pressure regulation of the first reversing pressure-reducing valve (4) and the second reversing pressure-reducing valve (5) is an electrical proportional regulation.
8. A control method of a multifunctional control system of a screed of a paver according to any one of claims 1 to 7, comprising the steps of:
1) The operator triggers a parking instruction through the console, and the controller immediately sends out an anti-climbing function instruction to the hydraulic control system to control the anti-climbing function of the screed plate;
2) The left lifting oil cylinder displacement sensor and the right lifting oil cylinder displacement sensor monitor the displacement of the screed plate in real time, and when the displacement detection value is larger than the measured value of the paving thickness before stopping, the controller sends a locking function instruction to the hydraulic control system to control the locking function of the screed plate; otherwise, continuing to control the anti-climbing function of the screed plate;
3) After stopping, until an operator triggers a starting instruction through an operating board, a controller delays for a set time and then sends a floating function instruction to a hydraulic control system to control a floating function of the screed;
4) The left lifting cylinder displacement sensor and the right lifting cylinder displacement sensor monitor the displacement of the screed plate in real time, when the displacement detection value is smaller than the paving thickness measurement value before stopping, the controller sends a power-assisting function instruction to the hydraulic control system to control the power-assisting function of the screed plate, the controller detects the power-assisting pressure of the screed plate according to the left lifting cylinder pressure sensor and the right lifting cylinder pressure sensor, and the power-assisting pressure is regulated by the hydraulic control system in real time along with the displacement change of the left lifting cylinder and the right lifting cylinder, so that the screed plate quickly enters a floating state; otherwise, continuing to control the floating function of the screed.
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| CN110042732B (en) * | 2019-04-04 | 2024-04-26 | 柳工无锡路面机械有限公司 | Intelligent heating system and method for road paver |
| CN110656558B (en) * | 2019-09-10 | 2024-04-26 | 江苏四明工程机械有限公司 | Four-crawler intelligent slipform paver and upright post floating electrohydraulic control system thereof |
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| CN202881828U (en) * | 2012-09-28 | 2013-04-17 | 天津山河装备开发有限公司 | Hydraulic system for controlling movement of ironing plate of road surface paver |
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