CN211778271U - Hydraulic traveling system of riding type road marking vehicle - Google Patents
Hydraulic traveling system of riding type road marking vehicle Download PDFInfo
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- CN211778271U CN211778271U CN201922311496.5U CN201922311496U CN211778271U CN 211778271 U CN211778271 U CN 211778271U CN 201922311496 U CN201922311496 U CN 201922311496U CN 211778271 U CN211778271 U CN 211778271U
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Abstract
The hydraulic traveling system of the riding type road marking vehicle comprises a hydraulic pump, a differential pressure overflow valve, an overflow valve, a pressure compensator, a proportional direction valve, an electric control handle and a hydraulic motor, wherein the position function in the proportional direction valve is Yx type, and a shuttle valve is connected between an A port and a B port of the proportional direction valve; to sum up, the utility model discloses a hydraulic system of engineering machine tool walking for control road marking line car advances, retreats, stops, and input current ramp signal's slope when control proportion direction valve proportion electromagnetism iron is expert, the outage, the speed when control hydraulic motor starts and stops, thereby reduce the impact when vehicle start and parking. Controlling the current of the proportional electromagnet to control the rotating speed of the hydraulic motor so as to control the speed of the vehicle; when the load of the hydraulic motor of the vehicle downhill is a negative load, the outlet back pressure of the hydraulic motor is balanced by the balance valve, so that the hydraulic motor rotates stably, and the vehicle speed is stable and easy to control.
Description
Technical Field
The utility model belongs to the technical field of engineering machine tool, concretely relates to ride formula road marking car hydraulic pressure traveling system that drives.
Background
The conventional hydraulic control principle is as shown in fig. 1, and comprises a hydraulic pump 1, a differential pressure overflow valve, an overflow valve, a pressure compensator, a proportional directional valve 2, an electric control handle and a hydraulic motor 3, wherein the middle position of the proportional directional valve is in an O shape, the hydraulic pump 1 supplies power to the hydraulic motor 3 through the proportional directional valve 2 to drive the hydraulic motor 3 to rotate, and the forward rotation, the reverse rotation, the stop and the magnitude of the forward and reverse rotation speed of the hydraulic motor 3 can be controlled by changing the electrification of proportional electromagnets YV1 and YV2 of the proportional directional valve 2 and controlling the magnitude of current, so as to control the forward, reverse, stop and forward and reverse speeds of the vehicle, and the magnitudes of currents of the proportional electromagnets YV1 and YV2 are controlled by the electric control handle.
When the electric control handle is in the middle position, the proportional electromagnets YV1 and YV2 are not electrified, the valve core of the proportional directional valve is in the middle position, the valve port is closed, the hydraulic pump can not supply oil to the hydraulic motor, the hydraulic motor can not rotate, and the vehicle stops.
When the electric control handle is pushed forwards, the proportional electromagnet YV1 is electrified, pilot pressure oil pushes the valve element to move downwards, the proportional direction valve works upwards, pressure oil output by the hydraulic pump enters the port A of the hydraulic motor through the port P and the port A of the proportional direction valve, return oil of the hydraulic motor passes through the port B of the hydraulic motor, the port B of the proportional direction valve and the port T of the hydraulic motor return oil tank, the pressure oil drives the hydraulic motor to rotate forwards, a vehicle moves forwards, the larger the angle of forward pushing of the electric control handle is, the larger the current of the proportional electromagnet YV1 is, the larger the opening of the proportional direction valve is, the larger the flow of the pressure oil entering the hydraulic motor through the proportional direction valve is, the higher the forward rotation speed of the hydraulic motor is, and the faster the forward speed of the.
When the electric control handle is pushed backwards, the proportional electromagnet YV2 is electrified, pilot pressure oil pushes the valve element to move upwards, the proportional direction valve works at the lower position, pressure oil output by the hydraulic pump enters the port B of the hydraulic motor through the port P and the port B of the proportional direction valve, return oil of the hydraulic motor passes through the port A of the hydraulic motor, the port A of the proportional direction valve and the port T of the return oil tank, the pressure oil drives the hydraulic motor to rotate reversely, a vehicle moves backwards, the larger the angle of forward pushing of the electric control handle is, the larger the current of the proportional electromagnet YV2 is, the larger the opening of the proportional direction valve is, the larger the flow of the pressure oil entering the hydraulic motor through the proportional direction valve is, the higher the reverse rotation speed of the hydraulic motor is, and the backward moving speed of the.
Although the conventional hydraulically-controlled ride-on road marking vehicle can normally mark construction work under most working conditions, the conventional hydraulically-controlled ride-on road marking vehicle has some problems and cannot normally perform construction under serious conditions.
1. When the vehicle starts or stops, the vehicle body is easy to shake sharply, the operation hand feeling is not good, and the reason for the situation is as follows:
when a driver operates the electric control handle to control the vehicle to start or stop, the wrist is supported on the operating platform beside the handle and is stable, and then the handle is slowly pushed forwards or pulled backwards, so that the phenomenon of forward and backward shaking cannot occur when the vehicle starts or stops. Otherwise, if the wrist is not stabilized and the push-pull handle is slightly faster, when the vehicle is controlled by the forward push handle to start, the vehicle suddenly moves forward, the body of the driver tilts backwards due to inertia, so that the handle is held by the hand to be pulled backwards, the vehicle is suddenly changed from forward to backward, and the vehicle shakes back and forth; when the vehicle is parked, the electric control handle is pulled to the middle position from the front position, the vehicle is suddenly changed from forward to stop, and due to inertia, the body of a driver leans forward, so that the driver holds the handle to push forwards, the vehicle is suddenly changed into forward, and the vehicle shakes back and forth; the operation hand feeling is not good, and the operation of a new driver for the first time is not suitable.
2. When the vehicle is used for marking construction on a downhill, the speed of the vehicle cannot be controlled, the vehicle is difficult to drive at a set speed, and marking construction cannot be carried out in serious cases, so that the reason for the condition is as follows:
when the vehicle runs downhill, the electric control handle is pushed forward, the proportional direction valve works upwards, pressure oil output by the hydraulic pump enters the port A of the hydraulic motor through the port P and the port A of the proportional direction valve, return oil of the hydraulic motor returns to an oil tank through the port B of the hydraulic motor, the port B of the proportional direction valve and the port T, and the hydraulic motor is driven to rotate forwards. Because the vehicle can slide downwards even without driving force when the component force of the gravity of the vehicle along the inclined plane is larger than the friction force of the road surface, and the hydraulic motor rotates faster and the vehicle stalls under the condition that the opening degree of the valve port of the proportional direction valve is larger and the oil return resistance of the hydraulic motor is small, an electric control handle needs to be operated to control the valve port of the proportional direction valve to be smaller, the oil return resistance of the hydraulic motor is increased, and the vehicle speed is slowed. At the moment, the oil inlet flow of the hydraulic motor is relatively small, the inlet pressure is relatively low, the pressure output by the hydraulic pump is also relatively low according to the conventional principle, but because the load of the hydraulic motor is a negative load, the outlet pressure of the hydraulic motor is higher than the inlet pressure, and the pressure fed back to the pressure compensator and the differential pressure overflow valve in the proportional direction valve is the outlet pressure of the hydraulic motor, the pressure output by the hydraulic pump is higher, the opening of the pressure compensator is relatively large, although the opening degree of the valve port of the proportional direction valve is relatively small, the pressure transmitted to the inlet of the hydraulic motor is still higher, the hydraulic motor still rotates faster, an electric control handle needs to be continuously operated, and even a vehicle needs to be stopped for a short time, so that. It is difficult to maneuver the vehicle downhill.
3. When a vehicle is parked on a slope, a situation of rolling downhill occurs, which is caused by the following reasons:
the vehicle stops on a slope, when the slope reaches a certain angle, the component force of the gravity of the vehicle along the slope is greater than the friction force of the road surface, the vehicle has a downward movement trend, the hydraulic motor is driven by the force to be in a pump working condition, the proportional direction valve is in a middle position, the valve port is closed, the motor outlet generates pressure to prevent the motor outlet from rotating, the outlet pressure of the motor is increased along with the increase of the slope, although the middle position of the proportional direction valve is in an O-shaped function, a motor outlet channel is closed, the hydraulic motor cannot rotate, but the motor does not have a mechanical brake because the vehicle does not have a parking brake, the structure of the motor cannot be completely closed, leakage exists, the motor shaft slowly rotates after the leakage lasts for a long time, and the vehicle slips.
SUMMERY OF THE UTILITY MODEL
The utility model discloses a solve the weak point among the prior art, provide a job stabilization, avoid the ride formula road marking car hydraulic pressure traveling system on vehicle swift current slope.
In order to solve the technical problem, the utility model adopts the following technical scheme: the hydraulic traveling system of the riding type road marking vehicle comprises a hydraulic pump, a differential pressure overflow valve, an overflow valve, a pressure compensator, a proportional direction valve, an electric control handle and a hydraulic motor, wherein the hydraulic pump is respectively connected with the differential pressure overflow valve, the pressure compensator and the overflow valve through pipelines, the connecting pipelines of the pressure compensator, the differential pressure overflow valve and the overflow valve are connected in parallel, the hydraulic pump is connected with the hydraulic motor through an oil outlet pipeline, the proportional direction valve is connected onto the oil outlet pipeline, a shuttle valve is connected between an A port and a B port of the proportional direction valve, a balance valve is installed between an oil inlet pipeline and an oil return pipeline of the hydraulic motor, a hydraulic brake is arranged on the hydraulic motor, and the hydraulic brake is connected with the shuttle valve through a control.
The median function of the proportional directional valve is Yx type.
And the control oil circuit of the hydraulic brake and the shuttle valve is also connected with an electromagnetic directional valve.
Adopt above-mentioned technical scheme, the utility model discloses following beneficial effect has: the speed of starting and stopping of the hydraulic motor can be controlled by controlling the slope of an input current slope signal when the proportional directional valve proportional electromagnet is powered on and powered off, so that the impact of starting and stopping of the vehicle is reduced; secondly, when the load of the hydraulic motor of the vehicle downhill is a negative load, the balance valve can balance the outlet back pressure of the hydraulic motor, so that the hydraulic motor rotates stably, and the vehicle speed is stable and easy to control; a hydraulic brake is added on an output shaft of the hydraulic motor, so that the situation of slope slipping is prevented when the vehicle stops on a slope; when the proportional direction valve is switched to the middle position according to a slope signal, pilot control oil of the balance valve is quickly released, and the balance valve is quickly closed; an electromagnetic directional valve is bypassed between the shuttle valve and the hydraulic brake, when the vehicle is stopped, the power can be cut off in a delayed mode according to the braking requirement, the brake is quickly and completely released when the time is up, and the hydraulic brake quickly brakes.
To sum up, the utility model discloses a hydraulic system of engineering machine tool walking for control road marking line car advances, retreats, stops, and input current ramp signal's slope when control proportion direction valve proportion electromagnetism iron is expert, the outage, the speed when control hydraulic motor starts and stops, thereby reduce the impact when vehicle start and parking. Controlling the current of the proportional electromagnet to control the rotating speed of the hydraulic motor so as to control the speed of the vehicle; when the load of the hydraulic motor of the vehicle downhill is a negative load, the outlet back pressure of the hydraulic motor is balanced by the balance valve, so that the hydraulic motor rotates stably, and the vehicle speed is stable and easy to control; when the vehicle is parked on a slope, the hydraulic brake is added on the output shaft of the hydraulic motor, so that the vehicle is prevented from sliding down the slope.
Drawings
FIG. 1 is a prior art hydraulic control schematic;
fig. 2 is a hydraulic control schematic diagram of the present invention.
Detailed Description
As shown in fig. 2, the utility model discloses a ride formula road marking car hydraulic pressure traveling system, including hydraulic pump 1, differential pressure overflow valve 4, overflow valve 5, pressure compensator 6, proportional direction valve 2, automatically controlled handle and hydraulic motor 3, the bit function is the Yx type in the proportional direction valve 2, be connected with shuttle valve 7 between proportional direction valve 2A mouth and the B mouth, install balanced valve 8 between hydraulic motor 3's the oil inlet way and the oil return way, be provided with hydraulic brake 9 on the hydraulic motor 3, hydraulic brake 9 is connected with shuttle valve 7 through the control oil circuit, still be connected with electromagnetic reversing valve 10 on hydraulic brake 9 and shuttle valve 7's the control oil circuit.
When a vehicle starts or stops, the vehicle body shakes sharply forwards and backwards, and the solution is as follows: the electric control handle does not directly control the proportional electromagnet of the proportional directional valve 2, the electric control handle is operated, a control command is sent out, the command enters the controller, a ramp signal is generated, the given current of the proportional electromagnet is slowly increased along with the time through the ramp signal, the valve core of the proportional directional valve 2 is driven to be slowly opened or closed, the motor is controlled to be slowly started or stopped, and the vehicle is slowly started or stopped, so that the condition that the vehicle body shakes front and back severely is avoided, the slope of the ramp signal is adjustable, and the starting and stopping speed of the vehicle is adjusted.
When the vehicle is constructed by marking lines on a downhill, the speed of the vehicle cannot be controlled, and the solution is as follows: the balance valve 8 is added between the proportional direction valve 2 and the hydraulic motor 3, the balance valve 8 overcomes the pressure generated by the outlet B port of the hydraulic motor 3 due to negative load, the hydraulic motor 3 rotates stably and can not rotate faster, meanwhile, due to the addition of the balance valve 8, the pressure between the balance valve 8 and the outlet B port of the proportional direction valve 2 becomes smaller, the pressure fed back to the pressure compensator 6 and the differential pressure overflow valve 4 is the inlet pressure of the hydraulic motor 3, the pressure is the pressure for normal operation of the driving motor, the driving pressure required by the motor is great, the hydraulic pump 1 provides the required pressure, when the slope goes down, the driving pressure of the motor is smaller, the hydraulic pump 1 provides smaller pressure, and the pressure compensator 6 also automatically adjusts a proper opening according to the feedback pressure. When the speed of the vehicle is needed to be fast, the angle for pushing the electric control handle forwards is larger, and when the speed of the vehicle is needed to be slow, the angle for pushing the electric control handle forwards is smaller, so that the control of the speed of the vehicle is easy to realize.
When a vehicle stops on a slope, a slope slipping condition occurs, and the solution method is as follows: the position function of the proportional direction valve 2 is changed from an O-type function to a Yx-type function, a hydraulic brake 9 is added on an output shaft of the hydraulic motor 3, a shuttle valve 7 is added between the proportional direction valve 2 and a balance valve 8, meanwhile, an electromagnetic reversing valve 10 is added on a brake control oil path, the hydraulic brake 9 is added on the output shaft of the hydraulic motor 3, the brake locks the output shaft of the motor when the vehicle is stopped, the motor cannot rotate due to motor leakage, and therefore the slope slipping phenomenon when the vehicle is stopped on a slope is avoided. When the vehicle runs, no matter whether the vehicle runs forwards or backwards, the electromagnet YV3 of the electromagnetic directional valve 10 is electrified, one path of high-pressure oil in the port 2A, B of the proportional directional valve is selected through the shuttle valve 7, the motor brake is opened, the output shaft of the motor is unlocked, and the motor rotates under the driving of the oil pressure to drive the vehicle to run forwards or backwards. The function of the middle position of the proportional direction valve 2 is changed from an O-type function to a Yx-type function, and the purpose is that when the vehicle is stopped, as long as the proportional direction valve 2 is switched to the middle position according to a slope signal, pilot control oil of the balance valve 8 can be quickly released, and the balance valve 8 can be quickly closed. The purpose of increasing the electromagnetic directional valve 10 is that although the proportional directional valve 2 has a neutral position Yx type function, the pressure can be relieved, the neutral position pressure relief has throttling, the control oil in the hydraulic brake 9 is more, the pressure is difficult to be completely relieved in a short time, and the braking time is uncontrollable, so the electromagnetic directional valve 10 is added, the power can be cut off in a delayed manner when the vehicle is stopped according to the braking requirement, the pressure in the brake is quickly and completely relieved when the time is up, and the hydraulic brake 9 can quickly brake.
The present embodiment is not intended to limit the shape, material, structure, etc. of the present invention in any form, and all of the technical matters of the present invention belong to the protection scope of the present invention to any simple modification, equivalent change and modification made by the above embodiments.
Claims (3)
1. Ride formula road marking car hydraulic pressure traveling system of driving, including hydraulic pump, differential pressure overflow valve, pressure compensator, proportion direction valve, automatically controlled handle and hydraulic motor, the hydraulic pump is connected with differential pressure overflow valve, pressure compensator, overflow valve through the pipeline respectively, and the connecting line of pressure compensator, differential pressure overflow valve and overflow valve is parallelly connected, and the hydraulic pump is connected with hydraulic motor through oil outlet pipeline, is connected with proportion direction valve on oil outlet pipeline, its characterized in that: a shuttle valve is connected between the port A and the port B of the proportional directional valve, a balance valve is installed between an oil inlet path and an oil return path of the hydraulic motor, a hydraulic brake is arranged on the hydraulic motor, and the hydraulic brake is connected with the shuttle valve through a control oil path.
2. The ride-on road-marking vehicle hydraulic travel system of claim 1, wherein: the median function of the proportional directional valve is Yx type.
3. The ride-on road-marking vehicle hydraulic travel system of claim 1, wherein: and the control oil circuit of the hydraulic brake and the shuttle valve is also connected with an electromagnetic directional valve.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201922311496.5U CN211778271U (en) | 2019-12-20 | 2019-12-20 | Hydraulic traveling system of riding type road marking vehicle |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201922311496.5U CN211778271U (en) | 2019-12-20 | 2019-12-20 | Hydraulic traveling system of riding type road marking vehicle |
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| CN211778271U true CN211778271U (en) | 2020-10-27 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114352597A (en) * | 2022-01-25 | 2022-04-15 | 佳木斯大学 | Overload reverse impact valve and overload prevention method |
| CN115075330A (en) * | 2022-06-27 | 2022-09-20 | 徐州徐工挖掘机械有限公司 | Bidirectional driving steering control system and method and excavator |
| CN114352597B (en) * | 2022-01-25 | 2024-04-23 | 佳木斯大学 | Overload reverse impact valve and overload prevention method |
-
2019
- 2019-12-20 CN CN201922311496.5U patent/CN211778271U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114352597A (en) * | 2022-01-25 | 2022-04-15 | 佳木斯大学 | Overload reverse impact valve and overload prevention method |
| CN114352597B (en) * | 2022-01-25 | 2024-04-23 | 佳木斯大学 | Overload reverse impact valve and overload prevention method |
| CN115075330A (en) * | 2022-06-27 | 2022-09-20 | 徐州徐工挖掘机械有限公司 | Bidirectional driving steering control system and method and excavator |
| CN115075330B (en) * | 2022-06-27 | 2024-02-27 | 徐州徐工挖掘机械有限公司 | Bidirectional driving steering control system and method and excavator |
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