CN217207067U - Hydraulic control system of low-density material transportation semitrailer - Google Patents
Hydraulic control system of low-density material transportation semitrailer Download PDFInfo
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- CN217207067U CN217207067U CN202122947536.2U CN202122947536U CN217207067U CN 217207067 U CN217207067 U CN 217207067U CN 202122947536 U CN202122947536 U CN 202122947536U CN 217207067 U CN217207067 U CN 217207067U
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Abstract
The utility model discloses a low density material transportation semitrailer hydraulic control system, contain the back door switch hydro-cylinder that is used for controlling low density material transportation semitrailer back door switch, be used for controlling low density material transportation semitrailer cylinder pivoted cylinder hydraulic motor of unloading, be used for controlling the capstan winch hydraulic motor of low density material transportation semitrailer push pedal return of unloading, be used for controlling back door switch hydro-cylinder, the hydraulic control integrated package of cylinder hydraulic motor and capstan winch hydraulic motor action and be used for providing the hydraulic oil pump and the hydraulic tank of power for whole hydraulic control system. The utility model has the advantages that: the control is simple, the cost is low, and the problems of heating of a hydraulic system and system faults can be well solved.
Description
Technical Field
The utility model relates to a low density material transportation semitrailer technical field, specific saying so relates to a low density material transportation semitrailer hydraulic control system.
Background
At present, a hydraulic control system used by a domestic low-density material transportation semitrailer generally adopts a pressure reducing valve to realize high-low pressure control, adopts a mode of increasing a tensioning oil cylinder to ensure that a steel wire rope and a conveying belt are tightened, but the structure has the following problems:
1. when the pressure reducing valve works, the overflow pressure of the main overflow valve needs to be reached, and the redundant flow of the hydraulic system then overflows back to the hydraulic oil tank at high pressure, so that the hydraulic system can be heated seriously;
2. the adoption of the manner of increasing the tensioning oil cylinder can lead to the increase of the length of the steel wire rope, and simultaneously, a plurality of guide pulley mechanisms can be added, thus leading to the increase of the failure rate of the system.
SUMMERY OF THE UTILITY MODEL
To the problem in the background art, the utility model aims to provide a novel low density material transport semitrailer hydraulic control system.
In order to achieve the above purpose, the utility model adopts the technical proposal that:
a hydraulic control system of a low-density material transportation semi-trailer comprises a rear door switch oil cylinder for controlling the rear door switch of the low-density material transportation semi-trailer, a roller hydraulic motor for controlling the rotation of a discharging roller of the low-density material transportation semi-trailer, a winch hydraulic motor for controlling the returning of a discharging push plate of the low-density material transportation semi-trailer, a hydraulic control manifold block for controlling the rear door switch oil cylinder, the roller hydraulic motor and the winch hydraulic motor to act, and a hydraulic oil pump and a hydraulic oil tank for providing power for the whole hydraulic control system; the rear door switch oil cylinder, the roller hydraulic motor, the winch hydraulic motor, the hydraulic oil pump and the hydraulic oil tank are all connected with the hydraulic control integrated block, and the hydraulic oil pump is also respectively connected with the hydraulic oil tank and the power takeoff of the engine of the low-density material transportation semitrailer.
Furthermore, the hydraulic control integrated block comprises a main overflow valve, a main overflow valve electromagnetic directional valve, a sub-overflow valve electromagnetic directional valve, a back door electromagnetic directional valve, a discharging and returning electromagnetic directional valve, a one-way sequence valve, a two-way throttle valve, an oil inlet, an oil return port, a pressure measuring port, a back door cylinder rod extending interface, a back door cylinder rod contracting interface, a roller motor forward rotation interface, a roller motor reverse rotation interface, a winch motor forward rotation interface and a winch motor reverse rotation interface;
the oil inlet is respectively communicated with the pressure measuring port, an oil inlet of the main overflow valve, an oil inlet of the back door electromagnetic reversing valve, an oil inlet of the unloading and returning electromagnetic reversing valve and an oil outlet of the hydraulic oil pump;
the oil return port is respectively communicated with an oil outlet of the main overflow valve, an oil outlet of the electromagnetic reversing valve of the main overflow valve, an oil outlet of the branch overflow valve, an oil return port of the electromagnetic reversing valve of the rear door, an oil return port of the unloading and returning electromagnetic reversing valve and a reverse rotation port of the winch motor;
an oil inlet of the main overflow valve electromagnetic directional valve is communicated with an oil outlet of the main overflow valve;
the oil inlet of the branch overflow valve is communicated with the oil outlet of the electromagnetic reversing valve of the branch overflow valve, the oil inlet of the electromagnetic reversing valve of the branch overflow valve is communicated with the hydraulic control oil port of the main overflow valve, and the hydraulic control oil port of the main overflow valve is also communicated with the oil inlet of the main overflow valve;
an oil outlet a and an oil outlet b of the rear door electromagnetic reversing valve are respectively communicated with the two-way throttle valve, the two-way throttle valve is respectively communicated with the rear door oil cylinder rod extending interface and the rear door oil cylinder rod contracting interface, and the rear door oil cylinder rod extending interface and the rear door oil cylinder rod contracting interface are respectively communicated with the rod extending interface a and the rod contracting interface b of the rear door opening and closing oil cylinder;
an oil outlet a and an oil outlet b of the unloading and returning electromagnetic directional valve are respectively communicated with the drum motor forward rotation interface and a one-way sequence valve, and the one-way sequence valve is respectively communicated with the drum motor reverse rotation interface and the winch motor forward rotation interface;
the rotary drum motor forward rotation interface and the rotary drum motor reverse rotation interface are respectively communicated with a forward rotation interface a and a reverse rotation interface b of the rotary drum hydraulic motor;
and the winch motor forward rotation port and the winch motor reverse rotation port are respectively communicated with the winch hydraulic motor forward rotation port a and the winch hydraulic motor reverse rotation port b.
Furthermore, a pressure gauge is connected to the pressure measuring port.
Furthermore, a filter is connected between the hydraulic oil pump and the hydraulic oil tank.
Further, when the electromagnetic coil T0 of the electromagnetic directional valve of the main overflow valve and the electromagnetic coil TL of the electromagnetic directional valve of the sub overflow valve are not electrified, the inlet oil and the oil return port of the hydraulic control manifold block are communicated.
Further, when the electromagnetic coil T0 of the main relief valve electromagnetic directional valve is energized and the electromagnetic coil TL of the sub relief valve electromagnetic directional valve is not energized, the set pressure of the main relief valve is 30 MPa.
Further, when the electromagnetic coil T0 of the electromagnetic directional valve of the main overflow valve and the electromagnetic coil TL of the electromagnetic directional valve of the branch overflow valve are both electrified, the set pressure of the main overflow valve is 16 MPa.
Compared with the prior art, the utility model has the advantages that:
1. the hydraulic branch of the back door switch oil cylinder is provided with a two-way throttle valve to control the flow of hydraulic oil flowing into the back door switch oil cylinder, and the main overflow valve is provided with a branch overflow valve and an electromagnetic directional valve to control the redundant flow of the hydraulic oil of the system to overflow back to the hydraulic oil tank at low pressure so as to reduce the heating of the hydraulic system.
2. The one-way sequence valve is arranged on the hydraulic branch of the roller hydraulic motor and the winch hydraulic motor to perform dynamic balance control on the pressure of the hydraulic system so as to ensure that a winch steel wire rope and a roller conveying belt are tightened, an additional guide pulley is not required to be additionally arranged, and the failure rate of the hydraulic control system is effectively reduced.
Drawings
FIG. 1 is a schematic diagram of a hydraulic control system of a low-density material transport semitrailer of the utility model;
FIG. 2 is a schematic diagram of the oil path direction of the hydraulic control system of the low-density material transportation semitrailer of the present invention when the power takeoff is hung;
FIG. 3 is a schematic diagram of the oil path direction of the hydraulic control system of the low-density material transport semitrailer of the present invention when the rear door is opened;
fig. 4 is a schematic diagram of the oil path direction of the hydraulic control system of the low-density material transport semitrailer of the present invention when the rear door is closed;
FIG. 5 is a schematic diagram of the oil path direction of the hydraulic control system of the low-density material transport semitrailer of the present invention when the unloading push plate unloads materials;
fig. 6 is a schematic diagram of the oil path direction of the hydraulic control system of the low-density material transport semitrailer of the present invention when the unloading push plate is returned;
fig. 7 shows a specific application example of the hydraulic control system of the low-density material transportation semitrailer (with the rear door in a closed state);
fig. 8 shows a specific application example of the hydraulic control system of the semitrailer for transporting low-density materials (with the rear door in an open state);
in fig. 2 to 6, the broken line indicates the hydraulic oil path direction;
description of reference numerals:
1. a rear door opening and closing oil cylinder;
2. a drum hydraulic motor;
3. a winch hydraulic motor;
4. a hydraulic control integrated block;
4.1, a main overflow valve;
4.2, a main overflow valve electromagnetic directional valve;
4.3, dividing an overflow valve;
4.4, dividing an overflow valve and an electromagnetic directional valve;
4.5, a rear door electromagnetic reversing valve;
4.6, unloading and returning the electromagnetic directional valve;
4.7, a one-way sequence valve;
4.8, a bidirectional throttle valve;
5. a hydraulic oil pump;
6. a hydraulic oil tank;
7. a power takeoff;
8. a filter;
9. a pressure gauge;
100. a rear door;
200. a discharge drum;
300. a discharging push plate;
400. a hydraulic winch;
500. a carriage.
Detailed Description
In order to make the technical means, the creation features, the achievement purposes and the functions of the present invention easy to understand and understand, how to implement the present invention is further explained below with reference to the accompanying drawings and the detailed description.
Referring to fig. 1, the utility model provides a low density material transportation semitrailer hydraulic control system, contain back door switch hydro-cylinder 1 for controlling the 100 switches of low density material transportation semitrailer back door, be used for controlling the cylinder hydraulic motor 2 that low density material transportation semitrailer unloads the cylinder 200 and rotates, be used for controlling the capstan winch hydraulic motor 3 that low density material transportation semitrailer unloads push pedal 300 return, be used for controlling back door switch hydro-cylinder 1, cylinder hydraulic motor 2 and capstan winch hydraulic motor 3 hydraulic control integrated package 4 of action and be used for providing the hydraulic oil pump 5 and the hydraulic oil tank 6 of power for whole hydraulic control system; wherein, back door switch hydro-cylinder 1, cylinder hydraulic motor 2, capstan winch hydraulic motor 3, hydraulic oil pump 5 and hydraulic tank 6 all are connected with hydraulic control manifold block 4, and hydraulic oil pump 5 still is connected with hydraulic tank 6 and low density material transportation semitrailer engine power takeoff 7 respectively.
In the utility model, referring to fig. 1 to 6, the hydraulic control integrated block 4 comprises a main overflow valve 4.1 and a main overflow valve electromagnetic directional valve 4.2, a branch overflow valve 4.3 and a branch overflow valve electromagnetic directional valve 4.4, a back door electromagnetic directional valve 4.5, a discharging and returning electromagnetic directional valve 4.6, a one-way sequence valve 4.8, a two-way throttle valve 4.7, an oil inlet P, an oil return port T, a pressure measuring port P1, a back door cylinder rod extending port a1, a back door cylinder rod contracting port B1, a drum motor forward rotation port a2, a drum motor reverse rotation port B2, a winch motor forward rotation port A3 and a winch motor reverse rotation port B3;
the oil inlet P is respectively communicated with a pressure measuring port P1, an oil inlet of the main overflow valve 4.1, an oil inlet of the back door electromagnetic directional valve 4.5, an oil inlet of the unloading and return electromagnetic directional valve 4.6 and an oil outlet of the hydraulic oil pump 5;
the oil return port T is respectively communicated with an oil outlet of the main overflow valve 4.1, an oil outlet of the main overflow valve electromagnetic directional valve 4.2, an oil outlet of the branch overflow valve 4.3, an oil return port of the rear door electromagnetic directional valve 4.5, an oil return port of the unloading and return electromagnetic directional valve 4.6 and a winch motor reverse rotation port B3;
an oil inlet of the main overflow valve electromagnetic directional valve 4.2 is communicated with an oil outlet of the main overflow valve 4.1;
an oil inlet of the partial overflow valve 4.3 is communicated with an oil outlet of the partial overflow valve electromagnetic directional valve 4.4;
an oil inlet of the electromagnetic directional valve 4.4 of the branch overflow valve is communicated with a hydraulic control oil port of the main overflow valve 4.1;
the hydraulic control oil port of the main overflow valve 4.1 is also communicated with the oil inlet of the main overflow valve 4.1;
an oil outlet a and an oil outlet B of a rear door electromagnetic reversing valve 4.5 are respectively communicated with a two-way throttle valve 4.7, the two-way throttle valve 4.7 is respectively communicated with a rear door oil cylinder rod extending interface A1 and a rear door oil cylinder rod contracting interface B1, and a rear door oil cylinder rod extending interface A1 and a rear door oil cylinder rod contracting interface B1 are respectively communicated with a rod extending interface a and a rod contracting interface B of a rear door opening and closing oil cylinder 1;
an oil outlet a and an oil outlet B of the unloading and returning electromagnetic directional valve 4.6 are respectively communicated with a roller motor forward rotation interface A2 and a one-way sequence valve 4.8, and the one-way sequence valve 4.8 is respectively communicated with a roller motor reverse rotation interface B2 and a winch motor forward rotation interface A3; the roller motor forward rotation interface A2 and the roller motor reverse rotation interface B2 are respectively communicated with a forward rotation interface a and a reverse rotation interface B of the roller hydraulic motor 2; the winch motor forward rotation port a3 and the winch motor reverse rotation port B3 are respectively communicated with the forward rotation port a and the reverse rotation port B of the winch hydraulic motor 3.
The utility model discloses in, it is shown with reference to fig. 1 to 6, still be connected with a manometer 9 on pressure measurement mouth P1 for the oil pressure in the pipeline among the real-time supervision hydraulic system.
The utility model discloses in, it is shown with reference to fig. 1 to 6, still be connected with a filter 8 between hydraulic oil pump 5 and hydraulic tank 6 for filter the dregs in the hydraulic oil, prevent that the dregs from entering into hydraulic oil pump 5, cause the damage to the oil pump.
The utility model discloses in, when solenoid T0 of main overflow valve electromagnetic directional valve 4.2 and solenoid TL of branch overflow valve electromagnetic directional valve 4.4 all were not circular telegram, the import oil P and the oil return opening T of hydraulic control integrated package 4 communicate with each other, refer to fig. 2 and show that control system at this moment is in no pressure state.
The utility model discloses in, when the solenoid T0 circular telegram of main overflow valve electromagnetic directional valve 4.2, when branch overflow valve electromagnetic directional valve 4.4's solenoid TL did not circular telegram, main overflow valve 4.1's set pressure was 30MPa, was the operating condition of cylinder hydraulic motor 2 this moment.
The utility model discloses in, when solenoid T0 of main overflow valve electromagnetic directional valve 4.2 and solenoid TL of branch overflow valve electromagnetic directional valve 4.4 all switched on, main overflow valve 4.1's set pressure is 16MPa, is capstan winch hydraulic motor 3 or back door switch hydro-cylinder 1's operating condition this moment.
In the utility model, referring to fig. 3, when energizing the solenoid T0 of the main overflow valve electromagnetic directional valve 4.2, the solenoid TL of the branch overflow valve electromagnetic directional valve 4.4 and the cylinder rod extending solenoid T1 of the back door electromagnetic directional valve 4.5, for the back door opening operation state, the hydraulic oil path in the hydraulic control system at this moment is as follows:
hydraulic oil in a hydraulic oil tank 6 firstly enters a hydraulic oil pump 5 through a filter 8, then is pumped into a back door electromagnetic directional valve 4.5 through an oil inlet P of a hydraulic control manifold block 4 through the hydraulic oil pump 5, then flows out of an oil outlet a of the back door electromagnetic directional valve 4.5, and sequentially flows into a back door switch oil cylinder 1 through a two-way throttle valve 4.7 and a back door oil cylinder rod extending connector A1, so that the pressure of a cylinder rod extending cavity of the back door switch oil cylinder 1 is increased to push an oil cylinder rod of the back door switch oil cylinder 1 to extend outwards and drive the back door 100 to open upwards, and in the process that the back door 100 opens upwards, the hydraulic oil in a cylinder rod retracting cavity of the back door switch oil cylinder 1 flows out of a rod retracting connector B under the pushing of the oil cylinder rod, sequentially flows into the back door electromagnetic directional valve 4.5 through a back door oil cylinder rod retracting connector B1 and a two-way throttle valve 4.7, and finally flows back to the hydraulic oil from an oil tank of the back door electromagnetic directional valve 4.5 through an oil return opening of the hydraulic control manifold block 4T and flows back to the hydraulic oil return port T6.
In the utility model discloses in, refer to as shown in fig. 4, when for solenoid T0 of main overflow valve solenoid directional valve 4.2, divide overflow valve solenoid directional valve 4.4's solenoid TL and the solenoid T2 circular telegram of the hydro-cylinder pole of back door solenoid directional valve 4.5, for the operating condition of back door closing, hydraulic circuit among the hydraulic control system at this moment moves towards as follows:
the hydraulic oil in the hydraulic oil tank 6 firstly enters the hydraulic oil pump 5 through the filter 8, then is pumped into the back door electromagnetic directional valve 4.5 through the hydraulic oil pump 5 through the oil inlet P of the hydraulic control integrated block 4, and then flows out of the oil outlet b of the back door electromagnetic directional valve 4.5, and flows into the back door switch oil cylinder 1 through a two-way throttle valve 4.7 and a back door oil cylinder rod contraction port B1, so that the pressure of the cylinder rod contraction cavity of the back door switch oil cylinder 1 is increased to drive the oil cylinder rod of the back door switch oil cylinder 1 to retract inwards and drive the back door 100 to close downwards, during the downward closing process of the rear door 100, the hydraulic oil in the rod extension chamber of the rear door switch cylinder 1 flows out from the rod extension port a under the pushing of the cylinder rod, and flows into a back door electromagnetic reversing valve 4.5 through a back door oil cylinder rod extension port A1 and a two-way throttle valve 4.7 in sequence, and finally, the oil flows back to the hydraulic oil tank 6 from the oil return port of the back door electromagnetic reversing valve 4.5 through the oil return port T of the hydraulic control integrated block 4.
In the utility model discloses in, refer to as shown in fig. 5, when giving solenoid T0 of main overflow valve solenoid directional valve 4.2 and unloading and the solenoid T3 circular telegram of return solenoid directional valve 4.6, for the operating condition of unloading, hydraulic pressure oil circuit among the hydraulic control system at this moment moves towards as follows:
hydraulic oil in the hydraulic oil tank 6 firstly enters the hydraulic oil pump 5 through the filter 8, then is pumped into the unloading and returning electromagnetic directional valve 4.6 through the hydraulic oil pump 5 through the oil inlet P of the hydraulic control integrated block 4, and then flows to the drum hydraulic motor 2 from the oil outlet a of the unloading and returning electromagnetic directional valve 4.6 through the drum motor forward rotation interface a2, and the drum hydraulic motor 2 at this time rotates forward under the pressure action of the hydraulic oil to carry out unloading operation (namely, the drum hydraulic motor 2 at this time drives the unloading drum 200 to rotate forward, and then the unloading drum 200 pulls the unloading push plate 300 together through the conveyer belt to retreat towards the back door 100 to carry out unloading); in the process of forward rotation of the roller hydraulic motor 2, hydraulic oil in the roller hydraulic motor 2 flows from the roller hydraulic motor 2 to the roller motor reverse rotation interface B2, then returns to the unloading and returning electromagnetic directional valve 4.6 through the roller motor reverse rotation interface B2 via the one-way sequence valve 4.8, and finally returns to the hydraulic oil tank 6 from an oil return port of the unloading and returning electromagnetic directional valve 4.6 via an oil return port T of the hydraulic control integrated block 4; in addition, because the hydraulic winch (not shown in the figure) is connected with the discharging push plate 300 through the winch steel wire rope), in the process that the drum hydraulic motor 2 pulls the discharging push plate 300 to retreat and discharge through the discharging drum 200 and the conveying belt, the hydraulic winch is driven by the winch steel wire rope to loosen the rope and rotate, namely, the winch hydraulic motor 3 is driven to rotate reversely, and the hydraulic principle shows that the winch hydraulic motor 3 can suck oil from the winch motor reverse rotation port B3 and discharge oil from the winch motor forward rotation port A3.
The utility model discloses in, refer to fig. 6 and show, when giving solenoid T0 of main overflow valve electromagnetic directional valve 4.2, dividing overflow valve electromagnetic directional valve 4.4's solenoid TL and unloading and return electromagnetic directional valve 4.6's solenoid T4 circular telegram, for return operating condition, hydraulic pressure oil circuit among the hydraulic control system at this moment moves towards as follows:
the hydraulic oil in the hydraulic oil tank 6 enters the hydraulic oil pump 5 through the filter 8, then is pumped into the unloading and returning electromagnetic directional valve 4.6 through the hydraulic oil pump 5 through the oil inlet P of the hydraulic control manifold 4, then flows to the winch hydraulic motor 3 from the oil outlet B of the unloading and returning electromagnetic directional valve 4.6 through the winch motor forward rotation interface A3, and then flows into the winch motor reverse rotation interface B3 through the winch hydraulic motor 3, when the pressure of the winch motor forward rotation interface A3 continues to increase, the winch steel wire rope and the conveying belt are tightened, the drum hydraulic motor 2 is driven, at this time, the valve core of the one-way sequence valve 4.8 is opened under the system pressure, the hydraulic oil flowing out from the oil outlet B of the unloading and returning electromagnetic directional valve 4.6 flows into the winch hydraulic motor 3 and the drum hydraulic motor 2 from the winch forward rotation interface A3 and the drum motor reverse rotation interface B2 respectively, at this time, if the flow rate of the hydraulic oil flowing into the winch motor forward rotation interface A3 is larger, the linear speed of a winch steel wire rope at the hydraulic winch is larger than the linear speed of a conveying belt on the discharging roller, the pressure of the hydraulic system is increased, the opening degree of a valve core of the one-way sequence valve 4.8 is increased, when the opening degree of the valve core of the one-way sequence valve 4.8 is increased, the flow rate of the hydraulic oil flowing into the roller motor reverse rotation interface B2 is also increased, when the flow rate of the hydraulic oil flowing into the roller motor reverse rotation interface B2 is increased, the linear speed of the winch steel wire rope at the hydraulic winch is smaller than the linear speed of the conveying belt on the discharging roller, the pressure of the hydraulic system is reduced, the opening degree of the valve core of the one-way sequence valve 4.8 is reduced, and the hydraulic system is dynamically balanced due to the reciprocating motion.
In the present invention, the opening and closing time of the rear door opening and closing cylinder 1 is preferably 5 to 10 seconds.
In the present invention, the drum hydraulic motor 2 is preferably a plunger motor having a maximum system pressure of 30MPa and a system flow of 150L/min.
In the present invention, the winch hydraulic motor 3 is preferably a plunger motor with a maximum system pressure of 16MPa and a system flow of 40L/min.
In the present invention, referring to fig. 1, the main overflow valve electromagnetic directional valve 4.2 and the sub-overflow valve electromagnetic directional valve 4.4 are preferably two-position two-way electromagnetic directional valves.
In the utility model, referring to fig. 1, the back door electromagnetic directional valve 4.5 and the unloading and returning electromagnetic directional valve 4.6 are preferably three-position four-way electromagnetic directional valves.
In the present invention, referring to fig. 1, the one-way sequence valve 4.8 is formed by connecting a sequence valve and a one-way valve in parallel.
In the present invention, referring to fig. 1, the two-way throttle valve 4.7 is formed by connecting two one-way throttle valves in parallel, and each one-way throttle valve is formed by connecting one throttle valve and one-way valve in parallel.
As the utility model discloses low density material transport semitrailer hydraulic control system's a concrete application embodiment: referring to fig. 7 and 8, two rear door switch oil cylinders 1 are symmetrically arranged on the left side and the right side of a carriage 500 of the low-density material transportation semi-trailer, and one end of each rear door switch oil cylinder 1 is hinged with a rear door 100, and the other end is hinged with the carriage; the roller hydraulic motor 2 is arranged at the rear end of a carriage 500 of the low-density material transportation semitrailer and is connected with the unloading roller 200, and the unloading roller 200 is connected with the rear end of the unloading push plate 300 through a conveying belt and is used for driving the unloading push plate 300 to retreat so as to realize unloading operation; winch hydraulic motor 3 sets up the carriage 400 front end at low density material transport semitrailer to link to each other with hydraulic winch 400, hydraulic winch 400 links to each other with the push pedal 300 front end of unloading through capstan winch wire rope, is used for driving the push pedal 300 of unloading and advances and realize the return operation.
Finally, the above description is only the embodiments of the present invention, not limiting the scope of the present invention, all the equivalent structures or equivalent processes that are used in the specification and the attached drawings or directly or indirectly applied to other related technical fields are included in the patent protection scope of the present invention.
Claims (7)
1. The utility model provides a low density material transportation semitrailer hydraulic control system which characterized in that: the device comprises a rear door switch oil cylinder (1) for controlling the opening and closing of a rear door (100) of the low-density material transportation semi-trailer, a roller hydraulic motor (2) for controlling the rotation of a discharging roller (200) of the low-density material transportation semi-trailer, a winch hydraulic motor (3) for controlling the returning of a discharging push plate (300) of the low-density material transportation semi-trailer, a hydraulic control manifold block (4) for controlling the movement of the rear door switch oil cylinder (1), the roller hydraulic motor (2) and the winch hydraulic motor (3), and a hydraulic oil pump (5) and a hydraulic oil tank (6) for providing power for the whole hydraulic control system;
wherein, back door switch hydro-cylinder (1), cylinder hydraulic motor (2), capstan winch hydraulic motor (3), hydraulic oil pump (5) and hydraulic tank (6) all are connected with hydraulic control integrated package (4), and hydraulic oil pump (5) still is connected with hydraulic tank (6) and low density material transportation semitrailer engine power takeoff (7) respectively.
2. The hydraulic control system of the low-density material transportation semitrailer of claim 1, characterized in that: the hydraulic control integrated block (4) comprises a main overflow valve (4.1), a main overflow valve electromagnetic directional valve (4.2), a sub overflow valve (4.3), a sub overflow valve electromagnetic directional valve (4.4), a back door electromagnetic directional valve (4.5), a discharging and returning electromagnetic directional valve (4.6), a two-way throttle valve (4.7), a one-way sequence valve (4.8), an oil inlet (P), an oil return port (T), a pressure measuring port (P1), a back door cylinder rod extension interface (A1), a back door cylinder rod contraction interface (B1), a roller motor forward rotation interface (A2), a roller motor reverse rotation interface (B2), a winch forward rotation motor interface (A3) and a winch motor reverse rotation interface (B3);
the oil inlet (P) is respectively communicated with the pressure measuring port (P1), an oil inlet of the main overflow valve (4.1), an oil inlet of the back door electromagnetic directional valve (4.5), an oil inlet of the unloading and return electromagnetic directional valve (4.6) and an oil outlet of the hydraulic oil pump (5);
the oil return port (T) is respectively communicated with an oil outlet of the main overflow valve (4.1), an oil outlet of the main overflow valve electromagnetic directional valve (4.2), an oil outlet of the branch overflow valve (4.3), an oil return port of the rear door electromagnetic directional valve (4.5), an oil return port of the unloading and return electromagnetic directional valve (4.6) and a winch motor reverse rotation port (B3);
an oil inlet of the main overflow valve electromagnetic directional valve (4.2) is communicated with an oil outlet of the main overflow valve (4.1);
an oil inlet of the branch overflow valve (4.3) is communicated with an oil outlet of the branch overflow valve electromagnetic directional valve (4.4), an oil inlet of the branch overflow valve electromagnetic directional valve (4.4) is communicated with a hydraulic control oil port of the main overflow valve (4.1), and the hydraulic control oil port of the main overflow valve (4.1) is also communicated with an oil inlet of the main overflow valve (4.1);
an oil outlet a and an oil outlet B of the rear door electromagnetic reversing valve (4.5) are respectively communicated with a two-way throttle valve (4.7), the two-way throttle valve (4.7) is respectively communicated with a rear door cylinder rod extending interface (A1) and a rear door cylinder rod contracting interface (B1), and the rear door cylinder rod extending interface (A1) and the rear door cylinder rod contracting interface (B1) are respectively communicated with a rod extending interface a and a rod contracting interface B of the rear door switch cylinder (1);
an oil outlet a and an oil outlet B of the unloading and returning electromagnetic directional valve (4.6) are respectively communicated with the drum motor forward rotation interface (A2) and a one-way sequence valve (4.8), and the one-way sequence valve (4.8) is respectively communicated with the drum motor reverse rotation interface (B2) and the winch motor forward rotation interface (A3);
the roller motor forward rotation interface (A2) and the roller motor reverse rotation interface (B2) are respectively communicated with the forward rotation interface a and the reverse rotation interface B of the roller hydraulic motor (2);
the winch motor forward rotation port (A3) and the winch motor reverse rotation port (B3) are respectively communicated with the winch hydraulic motor (3) forward rotation port a and the winch hydraulic motor (3) reverse rotation port B.
3. The hydraulic control system of the semitrailer for transporting low-density materials according to claim 2, is characterized in that: and the pressure measuring port (P1) is also connected with a pressure gauge (9).
4. The hydraulic control system of the semitrailer for transporting low-density materials according to claim 2, is characterized in that: a filter (8) is connected between the hydraulic oil pump (5) and the hydraulic oil tank (6).
5. The hydraulic control system of the low-density material transportation semitrailer of claim 2, characterized in that: when the electromagnetic coil T0 of the main overflow valve electromagnetic directional valve (4.2) and the electromagnetic coil TL of the branch overflow valve electromagnetic directional valve (4.4) are not electrified, the oil inlet (P) of the hydraulic control integrated block (4) is communicated with the oil return port (T).
6. The hydraulic control system of the low-density material transportation semitrailer of claim 2, characterized in that: when the electromagnetic coil T0 of the main overflow valve electromagnetic directional valve (4.2) is electrified and the electromagnetic coil TL of the branch overflow valve electromagnetic directional valve (4.4) is not electrified, the set pressure of the main overflow valve (4.1) is 30 MPa.
7. The hydraulic control system of the low-density material transportation semitrailer of claim 2, characterized in that: when the electromagnetic coil T0 of the main overflow valve electromagnetic directional valve (4.2) and the electromagnetic coil TL of the branch overflow valve electromagnetic directional valve (4.4) are electrified, the set pressure of the main overflow valve (4.1) is 16 MPa.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122947536.2U CN217207067U (en) | 2021-11-29 | 2021-11-29 | Hydraulic control system of low-density material transportation semitrailer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122947536.2U CN217207067U (en) | 2021-11-29 | 2021-11-29 | Hydraulic control system of low-density material transportation semitrailer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN217207067U true CN217207067U (en) | 2022-08-16 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122947536.2U Active CN217207067U (en) | 2021-11-29 | 2021-11-29 | Hydraulic control system of low-density material transportation semitrailer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN217207067U (en) |
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2021
- 2021-11-29 CN CN202122947536.2U patent/CN217207067U/en active Active
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