CN111152838B - Hydraulic integrated control device for mine car steering system and box lifting system - Google Patents
Hydraulic integrated control device for mine car steering system and box lifting system Download PDFInfo
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- CN111152838B CN111152838B CN201811326255.1A CN201811326255A CN111152838B CN 111152838 B CN111152838 B CN 111152838B CN 201811326255 A CN201811326255 A CN 201811326255A CN 111152838 B CN111152838 B CN 111152838B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/062—Details, component parts
- B62D5/063—Pump driven by vehicle engine
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60P—VEHICLES ADAPTED FOR LOAD TRANSPORTATION OR TO TRANSPORT, TO CARRY, OR TO COMPRISE SPECIAL LOADS OR OBJECTS
- B60P1/00—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading
- B60P1/04—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element
- B60P1/16—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element actuated by fluid-operated mechanisms
- B60P1/162—Vehicles predominantly for transporting loads and modified to facilitate loading, consolidating the load, or unloading with a tipping movement of load-transporting element actuated by fluid-operated mechanisms the hydraulic system itself
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/07—Supply of pressurised fluid for steering also supplying other consumers ; control thereof
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- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The application discloses a hydraulic integrated control device for a mine car steering system and a box lifting system, which comprises a large-flow pump, a small-flow pump, a reversing valve, a lifting converging valve, a steering gear, a balance valve group, a lifting oil cylinder and an oil tank. The application can select pumps with different flow rates according to the rotation speed of the engine, thereby effectively saving unnecessary power loss; meanwhile, the control system can comprehensively control the steering gear and the lifting oil cylinder, and can ensure the normal work of the steering gear and the lifting oil cylinder, so that potential safety hazards such as failure of the steering gear, too fast return of the lifting oil cylinder and the like are avoided under emergency conditions.
Description
Technical Field
The application relates to the technical field of mine car control, in particular to a hydraulic integrated control device for a mine car steering system and a box lifting system.
Background
The mine car is mainly suitable for engineering tunneling, construction and high-efficiency slag discharging transportation equipment of metallurgy, mines, coal mines, railways, highway tunnels, hydraulic culverts, underground mine galleries, military culverts and the like. With the rapid development of national economy, the mineral enterprises are pulled to advance suddenly, and particularly in recent years, large and medium-sized mineral industries are more and more like spring bamboo shoots after rain. The demand for mine cars as the primary carrier in the mining industry is also increasing.
The existing mine car diverter is mainly driven by a large-flow pump, mainly because higher hydraulic pressure is needed to drive the mine car to turn when the mine car is at a lower speed; however, when the rotation speed of the mine car engine is in a higher state, the steering gear can be controlled by only needing lower hydraulic pressure, and a large amount of unnecessary power loss can be caused by continuously using a large-flow pump, so that the operation cost is increased.
In addition, the lifting operation of the box body of the existing mine car is controlled by an independent lifting hydraulic system, so that the energy consumption is high, and the existing lifting hydraulic system cannot control the return speed, so that the efficiency is low.
Therefore, it is necessary to develop a hydraulic system combining steering and lifting.
Disclosure of Invention
The application aims to provide a hydraulic integrated control device of a mine car steering system and a box lifting system, which can select pumps with different flow rates according to the rotation speed of an engine, so that unnecessary power loss is effectively saved; meanwhile, the control system can comprehensively control the steering gear and the lifting oil cylinder, and can ensure the normal work of the steering gear and the lifting oil cylinder, so that potential safety hazards such as failure of the steering gear, too fast return of the lifting oil cylinder and the like are avoided under emergency conditions.
In order to achieve the above purpose, the application has the following beneficial effects:
the hydraulic integrated control device for the mine car steering system and the box lifting system comprises a large-flow pump, a small-flow pump, a reversing valve, a lifting converging valve, a steering gear, a balance valve group, a lifting oil cylinder, an oil tank and a motor for driving the large-flow pump and the small-flow pump;
the reversing valve is provided with an oil inlet P, P and an oil outlet A, B, C, the lifting converging valve is provided with an oil inlet E, D, an oil outlet T1 and an oil port F, G, the balance valve set is provided with oil ports P2 and H and oil outlets T2 and T3, and the steering gear is provided with an oil inlet J and an internal diversion oil return port T4;
the oil inlet P, P1 is respectively connected with the high-flow pump outlet and the low-flow pump outlet; the oil outlet A, B, C is respectively connected with the oil inlet J, the oil inlet D and the oil inlet E, the oil port F is connected with the oil inlet J, the oil port G is connected with the oil port P2 and the oil outlet T1, the oil outlets T1, T2, T3 and T4 are connected to an oil tank, and the oil port H is an oil inlet and outlet port of the lifting oil cylinder;
the reversing valve receives an engine rotating speed signal switching oil way, when the engine is in a low speed state, the oil inlet P is connected with the oil outlet A, B, the oil inlet P1 is connected with the oil outlet C, when the engine is in a high speed state, the oil inlet P is connected with the oil outlet C, and the oil inlet P1 is connected with the oil outlet B;
the lifting converging valve is provided with an upper position and a lower position, when the lifting converging valve is in the lower position, the oil inlet D is connected with the oil port F, the oil inlet E is connected with the oil port G, when the lifting converging valve is in the upper position, the oil inlet E is converged with the oil inlet D and is output from the oil port G to the oil port P2, the converging of the oil inlet E and the oil inlet D is also connected with the oil port F, and a first adjustable throttle valve is arranged on a liquid path connected with the oil port F;
the balance valve group is provided with a left position, a middle position and a right position, and when the balance valve group is in the middle position, the oil port P2 is connected to the oil outlet T3; when the lifting oil cylinder is in the left position, the oil port H is connected with the oil outlet T2 and the oil port P2 to form an oil return path of the lifting oil cylinder, and a first hydraulic lock and a second adjustable throttle valve are arranged on the oil return path of the lifting oil cylinder to form primary control of oil return of the lifting oil cylinder; and in the right position, the oil port P2 is connected with the oil port H to form an oil inlet path of the lifting oil cylinder.
The specific working principle of the application is as follows:
the diverter is internally provided with the internal diversion port T4, however, when the engine is in a high-speed state, the diversion port T4 cannot meet the liquid discharge requirement, so that the problems of abnormal sound, shaking and the like are caused, unnecessary power loss is caused, and therefore, the function of selecting a pump according to the rotating speed is required to be set.
When the engine is in a low-speed state, the large-flow pump supplies oil to the steering gear through a PAJ liquid path and a PBDFJ liquid path, the small-flow pump supplies oil to the lifting oil cylinder through a P1CEG, and at the moment, if the lifting oil cylinder does not need to act, the small-flow pump returns to the oil tank through a GP2T 3;
when the engine is in a high-speed state, the large-flow pump supplies oil to the lifting oil cylinder through the PCEG, the small-flow pump supplies oil to the steering gear through the P1BDF, and at the moment, if the lifting oil cylinder does not need to act, the large-flow pump returns to the oil tank through the GP2T 3;
the lifting oil cylinder controls oil inlet and outlet through the balance valve group, when the action is not needed, the oil returns to the oil cylinder through P2T3 at the middle position, and when the oil needs to be fed, the oil enters the oil cylinder through P2H at the right position; when oil is required to be discharged, oil is discharged through the left HP2GT1 and the left HT2, and a first hydraulic lock and a second adjustable throttle valve are arranged on an oil return liquid path of the lifting oil cylinder to form primary control of oil return of the lifting oil cylinder;
when the load of the lifting oil cylinder is large or the lifting oil cylinder needs to be lifted quickly, the lifting converging valve is adjusted to an upper position, the large-flow pump and the small-flow pump are converged in the lifting converging valve and supply oil for the lifting oil cylinder through the oil port G together, and meanwhile, the converged oil can flow out of the oil port F through the first adjustable throttle valve to supply oil for the steering gear continuously;
when the system stops working, oil in the steering gear enters the upper position of the lifting confluence valve through the oil port F and returns to the oil tank through the oil outlet T1 and the oil outlet T3 in the balance valve group.
Compared with the prior art, the application has the beneficial effects that:
1. according to the application, the output of the large-flow pump and the small-flow pump is controlled through the reversing valve, the large-flow pump supplies oil for the steering gear at low speed, and the small-flow pump supplies oil for the steering gear at high speed, so that the stable requirement of the steering gear on the oil flow can be well solved, the power can be saved, the heat can be reduced, the steering of the steering gear is more stable, and the abnormal problems of abnormal sound, shaking and the like caused by the fact that too much oil is directly supplied to the steering gear through the large-flow pump can be avoided, and the diversion of the steering gear can not meet the requirement of liquid discharge;
2. according to the application, the oil inlet and outlet and the operation stopping of the lifting oil cylinder are controlled through the balance valve group, the oil port H of the balance valve group timely lifts the oil inlet of the lifting oil cylinder and is the oil outlet of the lifting oil cylinder, the balance valve group ensures the working safety of the lifting oil cylinder, when in the middle position, the oil port H is closed, and in the emergency of oil pipe burst, pump failure and the like, the lifting oil cylinder can be kept in a static state, the conditions of quick falling back of the lifting oil cylinder and the like can not occur, and potential safety hazards are avoided;
3. according to the application, when the balance valve group is positioned at the left position, oil in the lifting oil cylinder is subjected to oil discharge operation through the first hydraulic lock and the second adjustable throttle valve, the oil discharge speed of the lifting oil cylinder can be controlled by the first hydraulic lock and the second adjustable throttle valve, so that the excessive or excessive slow return speed of the lifting oil cylinder is avoided, the quick-after-slow return speed is realized, and the potential safety hazard is avoided;
4. when the lifting oil cylinder works, the confluence branch of the large-flow pump and the small-flow pump still supplies oil to the steering gear through the first adjustable throttle valve, so that the steering action is prevented from being lost during lifting, the steering system is prevented from being invalid during unloading, the sudden emergency state is treated, and the driving safety is ensured;
the further improvement of the application is put into the following:
further, a second hydraulic lock is arranged between the oil port G and the oil outlet T1 to form secondary oil return control of the lifting oil cylinder.
Through adopting above-mentioned scheme, in lifting cylinder oil return in-process, carry out the secondary control through being equipped with the second hydraulic lock on liquid way GT1 to the oil return, avoid lifting cylinder oil return speed too fast, guarantee driving safety.
Further, the hydraulic fluid pump further comprises a spring type energy accumulator, wherein the spring type energy accumulator is provided with an oil port J1, and the oil port J1 is arranged on a liquid path connected with the oil port F and the main oil inlet J.
By adopting the scheme, the spring type energy accumulator charges when the oil supply hydraulic pressure of the steering gear is high, and supplies oil when the oil supply hydraulic pressure of the steering gear is low (when the lifting oil cylinder works), so that the steady flow effect is achieved, and the normal work of the steering gear is ensured; in addition, when the emergency such as pump failure, pipeline damage appear, the spring energy storage ware can guarantee that the steering gear can normal operating certain cycle, improves driving safety.
When the system stops working, high-pressure oil in the spring type energy accumulator enters the upper position of the lifting confluence valve through the oil port F and returns to the oil tank through the oil outlet T1 and the oil outlet T3 in the middle position of the balance valve group.
Further, a gravity sensor is arranged at the end part of the lifting oil cylinder and is electrically connected with the balance valve group, when the gravity sensor detects that the lifting pressure is greater than a set value range, the gravity sensor controls the balance valve group to be sequentially adjusted to the middle position and the left position, and the first hydraulic lock, the second adjustable throttle valve and the second hydraulic lock are matched to control the shaking of the lifting oil cylinder.
Through adopting above-mentioned scheme, when lifting cylinder promotes the box during operation, internal pressure continuously reduces, exists corresponding relation between hydro-cylinder top power and the angle of lifting, detect hydro-cylinder top power through gravity sensor, if surpass the settlement error, it has a large amount of earth or heavy object etc. probably to adhere on the box, gravity sensor can control balanced valves and adjust to the middle position in proper order and left bit this moment, keep controlling lifting cylinder, afterwards control lifting cylinder oil return, form the turbulent flow under the cooperation of first hydraulic lock on the oil return liquid way, second adjustable throttle valve and second hydraulic lock, lead to the shake of piston and box, thereby shake heavy object and earth out.
Further, the system safety valve is further arranged, an inlet of the system safety valve is connected with the outlet of the large-flow pump and the outlet of the small-flow pump respectively, a one-way valve is further arranged between the outlet of the small-flow pump and the inlet of the system safety valve, and an outlet of the system safety valve is connected with an oil tank to form primary pressure relief protection.
By adopting the scheme, the system safety valve can release pressure for the liquid path when the pump pressure is overlarge, so that the system safety is ensured.
Further, the hydraulic oil pump further comprises a steering gear safety valve, an inlet of the steering gear safety valve is connected with an oil inlet liquid path of the steering gear, and an outlet of the steering gear safety valve is connected with an oil tank to form a secondary pressure relief protection.
Through adopting above-mentioned scheme, steering gear relief valve can be when steering gear fuel feeding pressure is too big, for the liquid way pressure release, guarantees the work safety of steering gear.
Further, the engine control system also comprises a rotating speed signal converter, and the reversing valve receives an engine ECU signal through the rotating speed signal converter.
Furthermore, a filter is further arranged on the oil tank, the filter is provided with an oil inlet K1 and an oil outlet K2, the oil outlet T3 or T4 is connected with the oil inlet K1, and the oil outlet K2 is connected with the oil tank.
By adopting the scheme, the return filter can filter return oil, so that the cleanness of oil in the oil tank is ensured; one of the oil outlets T3 or T4 is selected to be connected with K1, and is mainly used for supplying oil to the steering gear when the large-flow pump supplies oil to the steering gear and the small-flow pump does not execute action, so that the oil in the oil tank can be filtered on line in real time, the whole oil tank is clean, and other loops can be directly connected with an oil return port without effectively reducing the oil return pressure through a filter element.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below. Like elements or portions are generally identified by like reference numerals throughout the several figures. In the drawings, elements or portions thereof are not necessarily drawn to scale.
Fig. 1 is a schematic structural view of an embodiment of the present application.
Fig. 2 is an enlarged partial schematic view of a in fig. 1.
Fig. 3 is an enlarged partial schematic view of b in fig. 1.
Fig. 4 is a lifting schematic of an embodiment of the application.
The figure shows:
1. a high flow pump; 2. a small flow pump; 3. a reversing valve; 4. lifting the converging valve; 5. a diverter; 6. a balancing valve group; 7. lifting the oil cylinder; 8. an oil tank; 9. a first adjustable throttle valve; 10. a first hydraulic lock; 11. a second adjustable throttle valve; 12. a second hydraulic lock; 13. a spring accumulator; 14. a system safety valve; 15. a one-way valve; 16. a diverter safety valve; 17. a back filter; 18. a rotational speed signal converter; 19. a motor; A. lifting angle.
Detailed Description
Embodiments of the technical scheme of the present application will be described in detail below with reference to the accompanying drawings. The following examples are only for more clearly illustrating the technical aspects of the present application, and thus are merely examples, and are not intended to limit the scope of the present application.
It is noted that unless otherwise indicated, technical or scientific terms used herein should be given the ordinary meaning as understood by one of ordinary skill in the art to which this application belongs.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. In the description of the present application, the meaning of "plurality" is two or more unless specifically defined otherwise.
Fig. 1 is a schematic structural view of an embodiment of the present application.
Fig. 2 is an enlarged partial schematic view of a in fig. 1.
Fig. 3 is an enlarged partial schematic view of b in fig. 1.
Fig. 4 is a lifting schematic of an embodiment of the application.
As shown in fig. 1 to 4, the hydraulic integrated control device for a mine car steering system and a box lifting system provided in this embodiment includes a large-flow pump 1, a small-flow pump 2, a reversing valve 3, a lifting confluence valve 4, a steering gear 5, a balancing valve group 6, a lifting cylinder 7, an oil tank 8, and a motor 19 for driving the large-flow pump 1 and the small-flow pump 2.
The displacement of the large-flow pump 1 is 40CC or more, and the displacement of the small-flow pump 2 is 20CC or less.
The reversing valve 3 is provided with an oil inlet P, P1 and an oil outlet A, B, C.
The lift confluence valve 4 is provided with an oil inlet E, D, an oil port F, T1 and an oil port G.
The balance valve group 6 is provided with an oil port P2, oil outlets T2 and T3 and an oil port H.
The diverter 5 is provided with an oil inlet J and an internal shunt oil return T4.
The outlet of the large-flow pump 1 is connected with the oil inlet P, and the outlet of the small-flow pump 2 is connected with the oil inlet P1; the oil outlet A, B, C is respectively connected with an oil inlet J, an oil inlet D and an oil inlet E, the oil port F is connected with the oil inlet J, the oil port G is connected with the oil port P2 and the oil port T1, the oil outlets T1, T2, T3 and T4 are connected to the oil tank 8, and the oil port H is an oil inlet and outlet port of the lifting oil cylinder 7.
The reversing valve 3 receives an engine rotating speed signal switching oil way, when the engine is in a low speed state, the oil inlet P is connected with the oil outlet A, B, the oil inlet P1 is connected with the oil outlet C, and when the engine is in a high speed state, the oil inlet P is connected with the oil outlet C, and the oil inlet P1 is connected with the oil outlet B;
the lifting confluence valve 4 is provided with an upper position and a lower position, when the lifting confluence valve is in the lower position, the oil inlet D is connected with the oil port F, the oil inlet E is connected with the oil port G, when the lifting confluence valve is in the upper position, the oil inlet E is converged with the oil inlet D and supplies oil for the lifting oil cylinder 7 through the oil port G, meanwhile, the converged fluid can flow out of the oil port F through the first adjustable throttle valve 11 to continuously supply oil for the steering gear 5, and a first adjustable throttle valve 9 is arranged on a fluid path connected with the converged fluid port F;
the balance valve group 6 is provided with a left position, a middle position and a right position, and when in the middle position, the oil port P2 is connected to the oil outlet T3; when the hydraulic jack is at the left position, the oil port H is connected with the oil outlet T2 and the oil port P2 to form an oil return path of the lifting oil cylinder 7, and a first hydraulic lock 10 and a second adjustable throttle valve 11 are arranged on the oil return path of the lifting oil cylinder 7 to form primary oil return control of the lifting oil cylinder 7; when the lifting device is at the right position, the oil port P2 is connected with the oil port H to form an oil inlet liquid path of the lifting oil cylinder 7.
The specific working principle of the application is as follows:
when the engine is in a low-speed state, the large-flow pump 1 supplies oil to the steering gear 5 through a PAJ liquid path and a PBDFJ liquid path, the small-flow pump 2 supplies oil to the lifting oil cylinder 7 through the P1CEG, and if the lifting oil cylinder 7 does not need to act, the oil of the small-flow pump 2 returns to the oil tank 8 through the GP2T 3;
when the engine is in a high-speed state, the large-flow pump 1 supplies oil to the lifting oil cylinder 7 through the PCEG, the small-flow pump 2 supplies oil to the steering gear 5 through the P1BDF, and if the lifting oil cylinder 7 does not need to act, the oil of the large-flow pump 1 returns to the oil tank 8 through the GP2T 3;
the lifting oil cylinder 7 controls oil inlet and outlet through the balance valve group 6, when no action is needed, oil returns to the oil tank 8 through the middle position P2T3, and when oil inlet is needed, the oil enters the lifting oil cylinder 7 through the right position P2H; when oil is required to be discharged, oil is discharged through the left HP2GT1 and the left HT2, and a first hydraulic lock 10 and a second adjustable throttle valve 11 are arranged on an oil return liquid path of the lifting oil cylinder 7 to form primary oil return control of the lifting oil cylinder 7;
when the load of the lifting oil cylinder 7 is large or the lifting oil cylinder needs to be lifted quickly, the lifting converging valve 4 is adjusted to be at an upper position, the large-flow pump 1 and the small-flow pump 2 are converged in the lifting converging valve 4 and supply oil to the lifting oil cylinder 7 through the oil port G together, and meanwhile, the converged oil can flow out of the oil port F through the first adjustable throttle valve 9 to continue to supply oil to the steering gear 5;
when the system stops working, the oil in the steering gear 5 enters the upper position of the lifting confluence valve 4 through the oil port F, and returns to the oil tank 8 through the oil outlet T1 and the oil outlet T3 in the balance valve group 6.
Further, in this embodiment, a second hydraulic lock 12 is disposed between the oil port G and the oil outlet T1 to form a second-stage control of oil return of the lifting cylinder 7.
In the oil return process of the lifting oil cylinder 7, the second hydraulic lock 12 is arranged on the liquid path GT1 to carry out secondary control on oil return, so that the too high oil return speed of the lifting oil cylinder 7 is avoided, and the driving safety is ensured.
Further, the embodiment is further provided with a spring type energy accumulator 13, the spring type energy accumulator 13 is provided with an oil port J1, and the oil port J1 is arranged on a liquid path where the oil port F is connected with the main oil inlet J.
The spring type energy accumulator 13 charges energy when the oil supply hydraulic pressure of the steering gear 5 is high, and supplies oil when the oil supply hydraulic pressure of the steering gear 5 is low (when the lifting oil cylinder works), so that the steady flow effect is achieved, and the normal work of the steering gear 5 is ensured; in addition, when the emergency such as pump failure, pipeline damage and the like occurs, the spring type energy accumulator 13 can ensure that the steering gear 5 can normally operate for a certain period, and the driving safety is improved.
When the system stops working, high-pressure oil in the spring type energy accumulator 13 enters the upper position of the lifting confluence valve 4 through the oil port F and returns to the oil tank 8 through the oil outlet T1 and the oil outlet T3 in the middle position of the balance valve group 6.
Further, a gravity sensor (not shown) is disposed at the end of the lifting cylinder 7, and is electrically connected with the balance valve group 6, and when the gravity sensor detects that the lifting pressure is greater than the set value range, the gravity sensor controls the balance valve group 6 to be sequentially adjusted to the middle position and the left position, and the first hydraulic lock 10, the second adjustable throttle valve 11 and the second hydraulic lock 12 cooperate to control the shaking of the lifting cylinder 7.
When the lifting cylinder 7 lifts the box body to work, the internal pressure is continuously reduced, the corresponding relation exists between the cylinder top force and the lifting angle, the cylinder top force is detected through the gravity sensor, if the set error is exceeded, a large amount of soil or heavy objects are possibly adhered on the box body, at the moment, the gravity sensor can control the balance valve group 6 to be sequentially adjusted to the middle position and the left position, the lifting cylinder 7 is controlled to be kept, then the lifting cylinder 7 is controlled to return oil, turbulence is formed under the cooperation of the first hydraulic lock 10, the second adjustable throttle valve 11 and the second hydraulic lock 12 on an oil return liquid path, the piston and the box body are caused to shake, and accordingly the heavy objects and the soil are shaken out.
As shown in fig. 4, when a heavy object (such as clay) cannot be discharged from the tank, under the condition of a certain lifting angle a, when the gravity sensor receives a range that the lifting pressure is greater than a set value, the balance valve set 6 is controlled to be sequentially switched to the middle position and the left position, then the lifting oil cylinder 7 returns oil under the action of the weight of the tank, turbulence is formed under the cooperation of the first hydraulic lock 10, the second adjustable throttle valve 11 and the second hydraulic lock 12 on the oil return liquid path, the lifting oil cylinder 7 is controlled to shake, and the heavy object is discharged.
Furthermore, the embodiment is further provided with a system safety valve 14, an inlet of the system safety valve 14 is respectively connected with an outlet of the large-flow pump 1 and an outlet of the small-flow pump 2, a one-way valve 15 is further arranged between the outlet of the small-flow pump 2 and the inlet of the system safety valve 14, and an outlet of the system safety valve 14 is connected with the oil tank 8 to form primary pressure relief protection.
The system safety valve 14 can release pressure for the liquid path when the pump pressure is excessive, so that the system safety is ensured.
Furthermore, the embodiment is also provided with a steering gear safety valve 16, an inlet of the steering gear safety valve 16 is connected with an oil inlet liquid path of the steering gear 5, and an outlet of the steering gear safety valve 16 is connected with the oil tank 8 to form a secondary pressure relief protection.
The steering gear safety valve 16 can be used for relieving pressure of a liquid path when the oil supply pressure of the steering gear 5 is overlarge, so that the working safety of the steering gear 5 is ensured.
Further, the present embodiment is also provided with a rotation speed signal converter 18, and the reversing valve 3 receives an engine ECU signal through the rotation speed signal converter 18, thereby switching the oil passage according to the engine rotation speed.
Further, a filter 17 is further arranged on the oil tank 8, the filter 17 is provided with an oil inlet K1 and an oil outlet K2, the oil outlet T3 or T4 is connected with the oil inlet K1, and the oil outlet K2 is connected with the oil tank 8.
The return filter 17 can filter return oil to ensure the cleanness of oil in the oil tank 8; one of the oil outlets T3 or T4 is selected to be connected with K1, and is mainly used for filtering the oil in the oil tank 8 on line in real time when the large-flow pump 1 supplies oil to the steering gear 5 and the small-flow pump 2 does not execute action, so that the whole oil tank is clean, other loops can be directly connected with an oil return port without a filter element, the oil return pressure is effectively reduced, and further, the system failure caused by oil pollution is further avoided.
In the description of the present application, numerous specific details are set forth. However, it is understood that embodiments of the application may be practiced without these specific details. In some instances, well-known methods, structures and techniques have not been shown in detail in order not to obscure an understanding of this description.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present application, and not for limiting the same; although the application has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the application, and are intended to be included within the scope of the appended claims and description.
Claims (6)
1. The hydraulic integrated control device for the mine car steering system and the box lifting system is characterized by comprising a large-flow pump, a small-flow pump, a reversing valve, a lifting converging valve, a steering gear, a balance valve group, a lifting oil cylinder, a spring type energy accumulator, an oil tank and a motor for driving the large-flow pump and the small-flow pump;
the reversing valve is provided with an oil inlet P, P and an oil outlet A, B, C, the lifting converging valve is provided with an oil inlet E, D, an oil outlet T1 and an oil port F, G, the balance valve set is provided with oil ports P2 and H and oil outlets T2 and T3, and the steering gear is provided with an oil inlet J and an internal diversion oil return port T4;
the oil inlet P, P1 is respectively connected with the high-flow pump outlet and the low-flow pump outlet; the oil outlet A, B, C is respectively connected with the oil inlet J, the oil inlet D and the oil inlet E, the oil port F is connected with the oil inlet J, the oil port G is connected with the oil port P2 and the oil outlet T1, the oil outlets T1, T2, T3 and T4 are connected to an oil tank, and the oil port H is an oil inlet and outlet port of the lifting oil cylinder;
the reversing valve receives an engine rotating speed signal switching oil way, when the engine is in a low speed state, the oil inlet P is connected with the oil outlet A, B, the oil inlet P1 is connected with the oil outlet C, when the engine is in a high speed state, the oil inlet P is connected with the oil outlet C, and the oil inlet P1 is connected with the oil outlet B;
the lifting converging valve is provided with an upper position and a lower position, when the lifting converging valve is in the lower position, the oil inlet D is connected with the oil port F, the oil inlet E is connected with the oil port G, when the lifting converging valve is in the upper position, the oil inlet E is converged with the oil inlet D and is output from the oil port G to the oil port P2, the converging of the oil inlet E and the oil inlet D is also connected with the oil port F, and a first adjustable throttle valve is arranged on a liquid path connected with the oil port F;
the balance valve group is provided with a left position, a middle position and a right position, and when the balance valve group is in the middle position, the oil port P2 is connected to the oil outlet T3; when the lifting oil cylinder is in the left position, the oil port H is connected with the oil outlet T2 and the oil port P2 to form an oil return path of the lifting oil cylinder, and a first hydraulic lock and a second adjustable throttle valve are arranged on the oil return path of the lifting oil cylinder to form primary control of oil return of the lifting oil cylinder; when the lifting oil cylinder is at the right position, the oil port P2 is connected with the oil port H to form an oil inlet path of the lifting oil cylinder;
a second hydraulic lock is arranged between the oil port G and the oil outlet T1 to form secondary oil return control of the lifting oil cylinder;
the spring type energy accumulator is provided with an oil port J1, and the oil port J1 is arranged on a liquid path connected with the oil port F and the oil port J.
2. The hydraulic integrated control device for a mine car steering system and a box lifting system according to claim 1, wherein a gravity sensor is arranged at the end part of the lifting cylinder and is electrically connected with the balance valve group, when the gravity sensor detects that the lifting pressure is greater than a set value range, the gravity sensor controls the balance valve group to be sequentially adjusted to a middle position and a left position, and the first hydraulic lock, the second adjustable throttle valve and the second hydraulic lock are matched to control the shaking of the lifting cylinder.
3. The hydraulic integrated control device for a mine car steering system and a box lifting system according to claim 1, further comprising a system safety valve, wherein an inlet of the system safety valve is connected with the large-flow pump outlet and the small-flow pump outlet respectively, a one-way valve is further arranged between the small-flow pump outlet and the inlet of the system safety valve, and an outlet of the system safety valve is connected with an oil tank to form a primary pressure relief protection.
4. The hydraulic integrated control device for a mine car steering system and a box lifting system according to claim 1, further comprising a steering gear safety valve, wherein an inlet of the steering gear safety valve is connected with an oil inlet liquid path of the steering gear, and an outlet of the steering gear safety valve is connected with an oil tank to form a secondary pressure relief protection.
5. A hydraulic integrated control device for a mine car steering system and a tank lifting system according to claim 1, further comprising a speed signal converter, and wherein the reversing valve receives engine ECU signals via the speed signal converter.
6. The hydraulic integrated control device for a bogie system and a box lifting system according to any one of claims 1 to 5, wherein a filter is further arranged on the oil tank, the filter is provided with an oil inlet K1 and an oil outlet K2, the oil outlet T3 or T4 is connected with the oil inlet K1, and the oil outlet K2 is connected with the oil tank.
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| CN201811326255.1A CN111152838B (en) | 2018-11-08 | 2018-11-08 | Hydraulic integrated control device for mine car steering system and box lifting system |
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| CN201811326255.1A CN111152838B (en) | 2018-11-08 | 2018-11-08 | Hydraulic integrated control device for mine car steering system and box lifting system |
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| CN111152838A (en) | 2020-05-15 |
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