Servo proportion system of mobile box

Abstract

The utility model discloses a mobile box servo proportion system. The system comprises a hydraulic oil tank storing hydraulic oil; a plurality of oil pumps fluidly connected to the hydraulic tank; a drive system operatively connected to the oil pump to provide power to the oil pump; the first control valve group is in fluid connection with the oil pump so as to adjust the flow and direction of the hydraulic oil from the oil pump; the pushing head system is in fluid connection with the first control valve group; the material lifting system is in fluid connection with the first control valve group; the controller is connected to the pushing head system, the material lifting system and the first control valve group; the controller is configured to control the first control valve group based on oil pressure in the push head system so as to adjust the number of the oil pumps providing hydraulic oil for the push head system.

Description

Technical Field

[0001] The present application relates to a mobile bin servo proportional system for transferring waste. Background Art

[0002] Most of the traditional mobile garbage bin hydraulic drive systems are three-phase AC motors driving quantitative pump systems. During the garbage compression process, the push head mechanism has to circulate and compress the garbage continuously. The collision noise generated by the structural parts of the push head mechanism, the vibration noise generated by the push head mechanism when switching, and the noise generated by the quantitative overflow of the hydraulic power are all relatively large. These noises will not only cause trouble to the surrounding residents, but also cause a large energy loss in the entire system, thereby reducing the operating efficiency and power utilization of the system. Utility Model Content

[0003] In view of the above-mentioned defects and shortcomings in the prior art, the present application provides a servo proportional system, which aims to solve the problems of high noise, large vibration, easy fatigue damage of structural parts and low power utilization rate generated by the push head mechanism of the existing mobile box during operation.

[0004] The present application provides a mobile box servo proportional system, comprising: a hydraulic oil tank, which stores hydraulic oil; a plurality of oil pumps, whose fluid is connected to the hydraulic oil tank; a drive system, which is operatively connected to the oil pump to provide power to the oil pump; a first control valve group, whose fluid is connected to the oil pump to adjust the flow and direction of the hydraulic oil from the oil pump; a push head system, whose fluid is connected to the first control valve group; a lifting system, whose fluid is connected to the first control valve group; and a controller, which is connected to the push head system, the lifting system and the first control valve group; wherein the controller is configured to control the first control valve group based on the oil pressure in the push head system to adjust the number of oil pumps that provide hydraulic oil to the push head system and the lifting system.

[0005] According to an optional embodiment, the first control valve group includes a single pump position and a multi-pump position; the first control valve group is configured to control one of the multiple oil pumps in the single pump position to provide hydraulic oil to the push head system, and control the remaining oil pumps in the multiple oil pumps to provide hydraulic oil to the lifting system; and the first control valve group is configured to control two or more of the multiple oil pumps in the multi-pump position to jointly provide hydraulic oil to the push head system, and control the remaining oil pumps in the multiple oil pumps to provide hydraulic oil to the lifting system.

[0006] According to an optional embodiment, the push head system includes: a push head control valve group, which is fluidically connected to the first control valve group; a plurality of push head cylinders, which are fluidically connected to the push head control valve group; and a push head mechanism, which is connected to the plurality of push head cylinders and performs linear movement with the aid of the plurality of push head cylinders.

[0007] According to an optional embodiment, the push head control valve group includes: a push head control one-way valve, which is configured to stabilize the flow of hydraulic oil in the push head control valve group to prevent pressure fluctuations generated during the switching process of the push head control valve group from impacting the oil pump; a push head differential switching valve, which is configured to control the differential operation between the multiple push head cylinders; a push head direction control valve, which is configured to control the moving direction of the push head mechanism; a push head control overflow valve, which is configured to ensure that the oil pressure in the push head system does not exceed the push head overflow pressure; and a push head system oil pressure sensor, which is integrated in the push head control valve group to measure the oil pressure in the push head system.

[0008] According to an optional embodiment, the lifting system includes: a lifting control valve group, which is fluidically connected to the first control valve group; a lifting cylinder, which is fluidically connected to the lifting control valve group; a balancing valve, which is arranged in a pipeline leading to the lifting cylinder; and a lifting mechanism, which is connected to the lifting cylinder and moves linearly with the aid of the lifting cylinder.

[0009] According to an optional embodiment, the lifting control valve group includes: a lifting control one-way valve, which is configured to stabilize the flow of hydraulic oil in the lifting control valve group and prevent pressure fluctuations generated during the switching of the lifting control valve group from impacting the oil pump; a proportional valve, which is configured to linearly control the flow of hydraulic oil flowing to the lifting cylinder; a logic valve, which is configured to manage the distribution of hydraulic oil according to demand, and jointly control the flow of hydraulic oil from the oil pump with the proportional valve so that the flow of hydraulic oil to the lifting cylinder is steplessly adjustable; a lifting direction control valve, which is configured to control the moving direction of the lifting mechanism; a lifting control overflow valve, which is configured to ensure that the oil pressure in the lifting system does not exceed the safe working pressure; a lifting system pressure sensor, which is integrated in the lifting control valve group to measure the oil pressure in the lifting system.

[0010] According to an optional embodiment, the drive system includes: a motor, which is operably connected to an oil pump to provide power to the oil pump; a motor controller, which is operably connected to the motor and is configured to adjust the speed and rotation direction of the motor; wherein the motor controller adjusts the speed of the motor based on the oil pressure in the push head system and the lifting system.

[0011] According to an optional embodiment, the moving box servo-proportional system includes two oil pumps.

[0012] The mobile box servo proportional system according to the present application is driven by a servo motor. The servo motor has the advantages of flexible control, rapid response, self-overload protection, etc., and can realize program control. The mobile box servo proportional system according to the present application can realize the switching of the dual pump differential and confluence during the movement of the push head mechanism, and control the moving speed of the push head mechanism in a variety of ways. The mobile box servo proportional system according to the present application can perform electrical proportional control on the lifting mechanism through a proportional valve to realize linear adjustment of the speed of the lifting mechanism. The mobile box servo proportional system according to the present application divides the entire garbage compression process into a light load fast forward compression stage, a medium speed compression stage and a strong compression stage, and can ensure that the compression rate will not decrease while realizing the gradient transformation of the pressure. At the same time, the mobile box servo proportional system according to the present application has a preset pressure lower than the overflow pressure, so that overflow loss does not occur, thereby obtaining a higher power utilization rate. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Although the present application may have various modifications and alternative forms, specific embodiments are shown by way of example in the drawings and described in detail. However, it should be understood that the drawings and detailed description are not intended to limit the present application to the specific forms disclosed. The present application is intended to cover all modifications, equivalents and substitutes within the spirit and scope of the present application as defined by the appended claims.

[0014] Figure 1 is a schematic diagram of a mobile box servo proportional system according to the present application. DETAILED DESCRIPTION

[0015] The exemplary embodiments of the present application will be described in more detail below with reference to the accompanying drawings. Although the exemplary embodiments of the present application are shown in the accompanying drawings, it should be understood that the present application can be implemented in various forms and should not be limited by the embodiments described here. On the contrary, these embodiments are provided in order to be able to more thoroughly understand the present application and to be able to fully convey the scope of the present application to those skilled in the art. It should be noted that when an element is referred to as "arranged in" another element, it can be directly in another element or indirectly in the other element. When an element is referred to as "fluid connected to" another element, their connection mode ensures that the fluid can flow between them. The terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, the features defined as "first" and "second" can expressly or implicitly include one or more of the features. In the description of the present application, the meanings of "multiple" and "several" are two or more, unless otherwise clearly and specifically defined.

[0016] Figure 1It is a schematic diagram of a mobile box servo proportional system according to the present application. The mobile box servo proportional system includes a hydraulic oil tank 1, a drive system 2, two oil pumps 3, a first control valve group 4, a push head system 5, a lifting system 6 and a controller 7. The hydraulic oil tank 1 stores hydraulic oil. The oil pump 3 is fluidly connected to the hydraulic oil tank 1. The drive system 2 is operatively connected to the oil pump 3 to provide power to the oil pump 3. The first control valve group 4 is fluidly connected to the oil pump 3 to control the flow and direction of the hydraulic oil from the oil pump 3. The push head system 5 is fluidly connected to the first control valve group 4 for compressing the garbage in the box. The lifting system 6 is fluidly connected to the first control valve group 4 for moving the hopper between the feeding position and the receiving position. It can be understood that an embodiment of a mobile box servo proportional system including multiple oil pumps 3 is also within the scope of protection of the present application, because its working principle is similar to that of a mobile box servo proportional system including two oil pumps 3.

[0017] The drive system 2 includes a motor and a motor controller. The motor is operably connected to the oil pump 3 for providing power to the oil pump 3. The motor controller is operably connected to the motor for adjusting the speed and rotation direction of the motor. Specifically, the motor controller determines the load condition of the motor based on the oil pressure in the pusher system 5 and the lifting system 6, and adjusts the speed of the motor based on the load condition of the motor to prevent the motor from being overloaded.

[0018] The first control valve group 4 includes a single pump position and a multi-pump position. In the single pump position, the first control valve group 4 controls one oil pump 3 to provide hydraulic oil to the push head system 5 to drive the push head system 5, and controls another oil pump 3 to provide hydraulic oil to the lifting system 6 to drive the lifting system 6. In the multi-pump position, the first control valve group 4 controls two oil pumps 3 to jointly provide hydraulic oil to the push head system 5 to drive the push head system 5. It can be understood that in the case where the mobile box servo proportional system includes more than two oil pumps 3, in the multi-pump position, the first control valve group 4 controls two or more oil pumps 3 to jointly provide hydraulic oil to the push head system 5 to drive the push head system 5, and controls the remaining oil pumps 3 to provide hydraulic oil to the lifting system 6 to drive the lifting system 6.

[0019] The push head system 5 includes a push head control valve group 51, two push head oil cylinders 52 and a push head mechanism (not shown). The push head control valve group 51 is fluidically connected to the first control valve group 4. The two push head oil cylinders 52 are fluidically connected to the push head control valve group 51. The push head mechanism is connected to the two push head oil cylinders 52 and moves linearly with the help of the two push head oil cylinders 52. It can be understood that the push head system 5 including more than two push head oil cylinders 52 is also within the protection scope of the present application, because its working principle is similar to that of the push head system 5 including two push head oil cylinders 52.

[0020] The push head control valve group 51 includes a push head control one-way valve, a push head differential switching valve, a push head direction control valve, a push head control overflow valve and a push head system oil pressure sensor. The push head control one-way valve is used to stabilize the flow of hydraulic oil in the push head control valve group 51 to prevent the pressure fluctuation generated during the switching process of the push head control valve group 51 from impacting the oil pump 3. Specifically, the push head control one-way valve can prevent the high-pressure oil from impacting the oil pump 3 when load fluctuation occurs during operation, and can also prevent one oil pump 3 from impacting the high-pressure oil in the other oil pump 3 during the switching process of the two oil pumps 3 merging to protect the oil pump 3. The push head differential switching valve is used to control the differential operation between the two push head oil cylinders 52. The push head direction control valve is used to control the moving direction of the push head mechanism. The push head control overflow valve is used to ensure that the oil pressure in the push head system 5 does not exceed the push head overflow pressure. The push head system oil pressure sensor is integrated in the push head control valve group 51 to measure the oil pressure in the push head system 5.

[0021] The lifting system 6 includes a lifting control valve group 61, a lifting cylinder 62, a balance valve 63 and a lifting mechanism (not shown). The lifting control valve group 61 is fluidically connected to the first control valve group 4. The lifting cylinder 62 is fluidically connected to the lifting control valve group 61. The balance valve 63 is arranged in a pipeline leading to the lifting cylinder 62. The lifting mechanism is connected to the lifting cylinder 62 and moves linearly with the help of the lifting cylinder 62.

[0022] The lifting control valve group 61 includes a lifting control one-way valve, a proportional valve, a logic valve, a lifting direction control valve, a lifting control overflow valve and a lifting system pressure sensor. The lifting control one-way valve is used to stabilize the flow of hydraulic oil in the lifting control valve group 61 to prevent the pressure fluctuation generated during the switching process of the lifting control valve group 61 from impacting the oil pump 3. Specifically, the lifting control one-way valve can prevent the high-pressure oil from impacting the oil pump 3 when the load fluctuates during operation, and can also prevent one oil pump 3 from impacting the high-pressure oil in the other oil pump 3 during the switching process of the two oil pumps 3 converging to protect the oil pump 3. The proportional valve is used to linearly control the flow of hydraulic oil flowing to the lifting cylinder 62. The logic valve is used to manage the distribution of hydraulic oil according to demand, and jointly control the flow of hydraulic oil from the oil pump 3 with the proportional valve, so that the flow of hydraulic oil flowing to the lifting cylinder 62 can be adjusted steplessly. The lifting direction control valve is used to control the moving direction of the lifting mechanism. The lifting control relief valve is used to ensure that the oil pressure in the lifting system 6 does not exceed the safe working pressure. The lifting system pressure sensor is integrated in the lifting control valve group 61 to measure the oil pressure in the lifting system 6.

[0023] The controller 7 is connected to the push head system 5, the material lifting system 6 and the first control valve group 4. The controller 7 controls the first control valve group 4 to switch between the single pump position and the multi-pump position based on the oil pressure in the push head system 5 to adjust the number of oil pumps that provide hydraulic oil to the push head system 5 and the material lifting system 6.

[0024] The method for controlling the mobile box servo proportional system according to the present application comprises the following steps:

[0025] Controlling the operation of the push head system 5 based on the stroke, speed and running time of the push head cylinder 52 in the push head system 5;

[0026] The operation of the material lifting system 6 is controlled based on the stroke, speed and running time of the material lifting cylinder 62 in the material lifting system 6 .

[0027] Specifically, the operation of controlling the pusher head system 5 includes the following steps:

[0028] When the push head system 5 does not receive the push head operation instruction, the oil pump 3 is unloaded at the middle position of the push head direction control valve, and the speed of the motor of the control drive system 2 is set to the first speed, so that the push head system 5 enters the waiting state;

[0029] The first operating mode and the second operating mode of the push head system 5 are switched based on the oil pressure in the push head system 5 measured by the push head system oil pressure sensor during the entire stroke of the push head cylinder 52. When the oil pressure in the push head system 5 is less than the preset pressure, the push head system 5 is controlled to operate in the first operating mode. When the oil pressure in the push head system 5 is greater than or equal to the preset pressure, the push head system 5 is controlled to operate in the second operating mode.

[0030] In the above steps, the preset pressure is less than the push head overflow pressure.

[0031] Controlling the push head system 5 to operate in the first operating mode includes the following steps:

[0032] In the first operation mode, after the drive system 2 receives the push head operation instruction, the first control valve group 4 is controlled to switch to the multi-pump position, so that the two oil pumps 3 jointly provide hydraulic oil to the push head control valve group 51, and the push head differential switching valve and the push head direction control valve in the push head control valve group 51 are controlled so that the two push head cylinders 52 are connected and extended in a differential manner, and the speed of the motor in the drive system 2 is changed from the first speed to the fourth speed;

[0033] After the two pusher head oil cylinders 52 extend for a first period of time, the pusher head differential switching valve is de-energized so that the two pusher head oil cylinders 52 are connected in a non-differential manner;

[0034] After the two push head oil cylinders 52 continue to extend for a second period of time, the first control valve group 4 is controlled to switch to the single pump position, so that one oil pump 3 alone supplies hydraulic oil to the push head control valve group 51, and the speed of the motor in the control drive system 2 is changed from the fourth speed to the first speed;

[0035] When the push head mechanism reaches the end position, the push head control valve group 51 is de-energized, and the oil pump 3 is controlled to unload;

[0036] After a certain period of time, the first control valve group 4 is controlled to switch to the multi-pump position, so that the two pusher cylinders 52 are retracted when the two oil pumps 3 jointly supply hydraulic oil to the pusher control valve group 51, and the speed of the motor in the drive system 2 is changed from the first speed to the fourth speed;

[0037] After the two push head oil cylinders 52 are retracted for a third period of time, the speed of the motor in the drive system 2 is changed from the fourth speed to the first speed, and the first control valve group 4 is controlled to switch to the single pump position, so that one oil pump 3 alone provides hydraulic oil to the push head control valve group 51;

[0038] After it is determined that the push head mechanism has returned to its position through the oil pressure change in the push head system 5 , the control valve group 5 is de-energized and the oil pump 3 is unloaded.

[0039] Controlling the push head system 5 to operate in the second operation mode includes the following steps:

[0040] In the second operation mode, after the drive system 2 receives the push head operation instruction, the first control valve group 4 is controlled to switch to the multi-pump position, so that the two oil pumps 3 jointly provide hydraulic oil to the push head control valve group 51, and the push head differential switching valve and the push head direction control valve in the push head control valve group 51 are controlled so that the two push head cylinders 52 are connected and extended in a differential manner, and the speed of the motor in the drive system 2 is changed from the first speed to the fourth speed;

[0041] When the oil pressure in the push head system 5 reaches the first set pressure as measured by the push head system oil pressure sensor, the push head differential switching valve is de-energized so that the two push head oil cylinders 52 are connected in a non-differential manner;

[0042] When the oil pressure in the push head system 5 reaches a second set pressure higher than the first set pressure as measured by the push head system oil pressure sensor, the first control valve group 4 is controlled to switch to the single pump position, so that one oil pump 3 alone supplies hydraulic oil to the push head control valve group 51, and the speed of the motor in the drive system 2 is changed from the fourth speed to the second speed;

[0043] After a certain period of time, the first control valve group 4 is controlled to switch to the multi-pump position, so that the two pusher cylinders 52 are retracted when the two oil pumps 3 jointly supply hydraulic oil to the pusher control valve group 51, and the speed of the motor in the drive system 2 is changed from the second speed to the fourth speed;

[0044] After the two pusher head cylinders 52 are retracted for a fourth period of time, the rotation speed of the motor in the drive system 2 is changed from the fourth rotation speed to the third rotation speed;

[0045] After it is determined that the push head mechanism has retracted into position through the oil pressure change in the push head system 5 , the rotation speed of the motor in the drive system 2 is changed from the third rotation speed to the first rotation speed, and the oil pump 3 is unloaded.

[0046] In the above steps, the first rotation speed<the second rotation speed<the third rotation speed<the fourth rotation speed, and the first set pressure<the second set pressure.

[0047] The operation of controlling the material lifting system 6 comprises the following steps:

[0048] Before the drive system 2 receives the material lifting operation instruction, the speed of the motor in the drive system 2 is set to a first speed;

[0049] After the drive system 2 receives the material lifting operation instruction, it controls the material lifting mechanism to accelerate linearly from static to rated moving speed;

[0050] After the lifting mechanism moves at the rated moving speed for a fifth period of time, the lifting mechanism is linearly decelerated according to the stroke control of the lifting cylinder 62;

[0051] After the lifting mechanism is determined to move to the upper stop position through the oil pressure change in the lifting system 6, the speed of the motor in the drive system 2 is changed from the first speed to the third speed, and the oil pump 3 is unloaded;

[0052] After a period of time, the material lifting control valve group 61 is controlled to make the material lifting mechanism move in the reverse direction, and the speed of the motor in the driving system 2 is changed from the third speed to the rated speed;

[0053] After the material lifting mechanism reaches the preset position, the speed of the motor in the drive system 2 is linearly decelerated from the rated speed;

[0054] After it is determined through the oil pressure change in the lifting system 6 that the lifting mechanism has moved to the lower stop position, the rotation speed of the motor in the drive system 2 is changed to the third rotation speed, and the oil pump 3 is unloaded.

[0055] When the system stops due to external reasons, the operation of controlling the material lifting system 6 includes the following steps:

[0056] When the feeding mechanism stops due to external reasons, the interruption process is entered;

[0057] In the interruption process, after the driving system 2 receives the material lifting operation instruction again, the material lifting mechanism is controlled to move at an idle speed lower than the rated moving speed;

[0058] After it is determined that the lifting mechanism has moved to the upper stop position or the lower stop position through the oil pressure change in the lifting system 6, the rotation speed of the motor in the driving system 2 is changed to the third rotation speed, and the oil pump 3 is unloaded.

[0059] In the above steps, the first speed < the third speed < the rated speed.

[0060] The application of the mobile box servo proportional system according to the present application is specifically described below with reference to the actual operation process of the material lifting system 6 of the mobile box servo proportional system.

[0061] When the garbage in the lifting mechanism is full and needs to be poured into the mobile box, start the motor and turn the lifting button to the lifting position. The lifting direction control valve in the lifting control valve group 61 is energized, and the opening of the proportional valve in the material control valve group 61 is gradually increased to the maximum, and the motor speed is controlled to uniformly reach the fifth speed greater than the first speed, so that the lifting cylinder 62 starts flexibly and smoothly in a short time. After the lifting cylinder 62 runs at a constant speed for a period of time, the time consumed for the extension and retraction of the lifting cylinder 62 during the entire stroke is calculated based on the parameters such as the stroke and running speed of the lifting cylinder 62 before, and the time consumed is corresponding to the extension length of the lifting cylinder 62. In this way, it can be determined that the lifting mechanism is about to reach the end of the stroke based on the extension length of the lifting cylinder 62. At this time, the proportional valve is controlled to reduce its opening. In this case, the pressure difference between the inlet and outlet of the proportional valve will gradually increase, and the change in the pressure difference will be reflected in the pilot oil chamber of the logic valve of the lifting control valve group 61, so that the force at both ends of the valve core of the logic valve changes, breaking the original balance. In this way, the valve core of the logic valve will overcome the spring force and move, so that the opening of the logic valve is opened, and the flow of the oil pump 3 is diverted. The smaller the opening of the proportional valve, the greater the pressure difference at both ends, so that the larger the opening of the logic valve, the less flow will flow into the lifting cylinder 62, resulting in a reduction in the running speed of the lifting cylinder 62. Since the opening of the proportional valve is controlled and changes linearly, the flow entering the lifting cylinder 62 also changes linearly, so that the lifting cylinder 62 can achieve stepless deceleration. After the lifting cylinder 62 decelerates for a period of time, the lifting cylinder 62 runs to the end of the stroke, so that the oil pressure in the lifting system 6 gradually increases. Based on the oil pressure in the lifting system 6 measured by the lifting system pressure sensor integrated in the lifting control valve group 61, the opening of the proportional valve is controlled to be linearly reduced to a specified value (for example, 1 / 4 opening), and the lifting direction control valve is de-energized. While the lifting cylinder 62 lifts the lifting mechanism into place, the oil pump 3 is unloaded through the logic valve. The whole process takes a short time, so the oil pressure in the material lifting system 6 will not reach the safe working pressure of the material lifting control overflow valve of the material lifting control valve group 61.

[0062] After the lifting mechanism is lifted into place and waits for a period of time, the lifting direction control valve is controlled to switch direction, and the opening of the proportional valve is linearly increased to the maximum value, so that the lifting mechanism begins to descend. After the lifting mechanism runs at a constant speed for a period of time, the end position of the lifting mechanism is determined based on the extension length of the lifting cylinder 62, the opening of the proportional valve is reduced to a specified value (for example, 1 / 4 opening), and the speed of the motor is changed to the first speed, so that the lifting cylinder 62 begins to decelerate. Based on the rise in oil pressure in the lifting system 6 measured by the lifting system pressure sensor integrated in the lifting control valve group 61, it is determined that the lifting cylinder 62 has run to the end of the stroke, the lifting direction control valve is de-energized, and the oil pump 3 is unloaded through the logic valve.

[0063] When the lifting mechanism encounters an emergency such as a sudden power failure of the control valve during the lifting or lowering process, the lifting cylinder 62 can be stopped in time at any position through the balance valve 63 of the lifting system 6. At this time, the lifting system 6 enters the interruption process, changes the speed of the motor of the drive system 2 to idle speed, and changes the opening of the proportional valve to the specified value. When the operator turns the lifting button to the lifting position or the lifting position again, the lifting cylinder 62 is controlled to rise or fall slowly. Based on the increase in oil pressure in the lifting system 6 measured by the lifting system pressure sensor integrated in the lifting control valve group 61, it is determined that the lifting cylinder 62 has run to the end of the stroke, the lifting direction control valve is de-energized, and the oil pump 3 is unloaded through the logic valve.

[0064] The application of the mobile box servo proportional system according to the present application is specifically described below with reference to the actual operation process of the push head system 5 of the mobile box servo proportional system.

[0065] The time taken for the extension and retraction of the push head oil cylinder 52 in the entire stroke is calculated based on parameters such as the stroke and running speed of the push head oil cylinder 52, and the time taken is corresponded to the extension length of the push head oil cylinder 52. When the oil pressure in the push head system 5 measured by the push head system oil pressure sensor integrated in the push head control valve group 51 is less than the preset pressure, it means that the amount of garbage in the compression chamber is small and the push head mechanism can be fully extended. In this case, the push head oil cylinder 52 is mainly controlled based on the position parameter, that is, the push head oil cylinder 52 is controlled in the first operating mode. When the oil pressure in the push head system 5 measured by the push head system oil pressure sensor integrated in the push head control valve group 51 is greater than or equal to the preset pressure, it means that the amount of garbage in the compression chamber is large and the push head mechanism cannot be fully extended. In this case, the push head oil cylinder 52 is mainly controlled based on the oil pressure in the push head system 5 measured by the push head system oil pressure sensor, that is, the push head oil cylinder 52 is controlled in the second operating mode.

[0066] In the first operation mode, after receiving the compression instruction, the speed of the motor of the drive system 2 is changed to the fourth speed, and the first control valve group 4 is switched to the multi-pump position so that the two oil pumps 3 jointly provide hydraulic oil to the push head control valve group 51. The differential valve in the push head control valve group 51 is switched so that the two push head oil cylinders 52 are connected in a differential manner and extend quickly. After the push head mechanism moves for a period of time, the push head oil cylinder 52 extends to the first position (for example, 60% of the full stroke of the push head oil cylinder 52). At this time, the differential valve in the push head control valve group 51 is de-energized so that the two push head oil cylinders 52 are no longer connected in a differential manner and run at a reduced speed. After the push head mechanism continues to move for a period of time, the push head oil cylinder 52 extends to the second position (for example, 90% of the full stroke of the push head oil cylinder 52). At this time, the first control valve group 4 is switched to the single pump position so that one oil pump 3 alone provides hydraulic oil to the push head control valve group 51, and the speed of the motor is changed to the first speed. After the push head mechanism continues to move for a period of time, the push head direction control valve in the push head control valve group 51 is controlled to switch direction, so that the push head control valve group 51 is powered, and the motor is changed to the fourth speed, so that the push head cylinder 52 starts to run in the reverse direction (retract). When the push head mechanism moves to the third position, the first control valve group 4 is kept in the single pump position, so that one oil pump 3 alone provides hydraulic oil to the push head control valve group 51, and the speed of the motor is changed to the third speed, so that the push head cylinder 52 starts to decelerate. After the push head mechanism continues to move for a period of time, it is determined that the push head cylinder 52 has reached the end of the stroke based on the oil pressure in the push head system 5 measured by the push head system oil pressure sensor, and the push head direction control valve is de-energized, so that the oil pump 3 is unloaded at the middle position of the push head direction control valve.

[0067] As the amount of garbage in the compression chamber increases, the push head cylinder 52 cannot be fully extended. In the second operating mode, the first control valve group 4 is switched to the multi-pump position so that the two oil pumps 3 jointly supply hydraulic oil to the push head control valve group 51. The speed of the motor is changed to the fourth speed. When the oil pressure in the push head system 5 reaches the first set pressure P1 measured by the push head system oil pressure sensor, the first control valve group 4 is switched to the single pump position so that one oil pump 3 alone supplies hydraulic oil to the push head control valve group 51. The push head cylinder 52 continues to move until the oil pressure in the push head system 5 reaches the second set pressure P2 measured by the push head system oil pressure sensor. In this case, the speed of the motor is changed to the second speed so that the push head mechanism runs at a reduced speed. When the oil pressure in the push head system 5 reaches the maximum preset pressure measured by the push head system oil pressure sensor, the timing starts. After a preset time period, the push head direction control valve in the push head control valve group 51 is controlled to switch its position, so that the first control valve group 4 switches to the multi-pump position, so that multiple oil pumps 3 jointly provide hydraulic oil to the push head control valve group 51. The motor speed is changed to the fourth speed, so that the push head cylinder 52 begins to retract. When the oil pressure in the push head system 5 is measured by the push head system oil pressure sensor, it means that the push head cylinder 52 has run into place. The motor speed is changed to the second speed, and the push head direction control valve is controlled to lose power, so that the oil pump 3 is unloaded at the middle position of the push head direction control valve.

[0068] The foregoing description of the embodiments has been provided for illustrative and descriptive purposes. It is not intended to be exhaustive or to limit the embodiments to the described variants. Many modifications and variations will be apparent to those skilled in the art. The embodiments are selected and described in order to best illustrate the principles and practical applications, so that those skilled in the art can understand the embodiments in their various embodiments and various modifications suitable for their intended use. Within the framework of the embodiments, the above-mentioned components and features can be combined between different embodiments.

Claims

1. A mobile box servo proportional system, comprising: A hydraulic oil tank (1) storing hydraulic oil; a plurality of oil pumps (3) fluidly connected to the hydraulic oil tank (1); a drive system (2) operatively connected to the oil pump (3) to provide power to the oil pump (3); a first control valve group (4) fluidly connected to the oil pump (3) to adjust the flow and direction of the hydraulic oil from the oil pump (3); A pusher head system (5) fluidly connected to the first control valve group (4); a feed system (6) fluidly connected to the first control valve group (4); and A controller (7) connected to the pusher system (5), the material lifting system (6) and the first control valve group (4); The controller (7) is configured to control the first control valve group (4) based on the oil pressure in the push head system (5) to adjust the number of oil pumps that provide hydraulic oil to the push head system (5) and the lifting system (6).

2. The mobile box servo proportional system according to claim 1, wherein: The first control valve group (4) includes a single pump position and a multi-pump position; The first control valve group (4) is configured to control one of the plurality of oil pumps (3) in a single pump position to supply hydraulic oil to the push head system, and to control the remaining oil pumps of the plurality of oil pumps (3) to supply hydraulic oil to the lifting system; as well as The first control valve group (4) is configured to control two or more oil pumps among the plurality of oil pumps (3) to jointly supply hydraulic oil to the push head system at the multi-pump position, and to control the remaining oil pumps among the plurality of oil pumps (3) to supply hydraulic oil to the lifting system.

3. The mobile box servo proportional system according to claim 1 or 2, wherein: The push head system (5) comprises: A pusher head control valve group (51), which is fluidically connected to the first control valve group (4); A plurality of push head cylinders (52) fluidly connected to the push head control valve group (51); and A push head mechanism is connected to the plurality of push head cylinders (52) and moves linearly with the aid of the plurality of push head cylinders (52).

4. The mobile box servo proportional system according to claim 3, wherein: The pusher head control valve group (51) comprises: A push head control one-way valve, which is configured to stabilize the flow of hydraulic oil in the push head control valve group (51) to prevent the pressure fluctuation generated during the switching process of the push head control valve group (51) from impacting the oil pump (3); A push head differential switching valve, configured to control the differential operation between the plurality of push head cylinders (52); A push head direction control valve configured to control the moving direction of the push head mechanism; A push head control relief valve configured to ensure that the oil pressure in the push head system (5) does not exceed a push head relief pressure; and The push head system oil pressure sensor is integrated in the push head control valve group (51) to measure the oil pressure in the push head system (5).

5. The mobile box servo proportional system according to claim 1 or 2, wherein: The material raising system (6) comprises: A feed control valve group (61) fluidly connected to the first control valve group (4); A lifting oil cylinder (62) which is fluidically connected to the lifting control valve group (61); A balancing valve (63) is arranged in the pipeline leading to the lifting cylinder (62); and The lifting mechanism is connected to the lifting cylinder (62) and moves linearly with the help of the lifting cylinder (62).

6. The mobile box servo proportional system according to claim 5, wherein: The material lifting control valve group (61) comprises: A material lifting control one-way valve, which is configured to stabilize the flow of hydraulic oil in the material lifting control valve group (61) to prevent the pressure fluctuation generated during the switching process of the material lifting control valve group (61) from impacting the oil pump (3); a proportional valve configured to linearly control the flow of hydraulic oil to the lifting cylinder (62); A logic valve configured to manage the distribution of hydraulic oil according to demand and to control the flow of hydraulic oil from the oil pump (3) together with the proportional valve so that the flow of hydraulic oil flowing to the lifting cylinder (62) is steplessly adjustable; A material lifting direction control valve configured to control the moving direction of the material lifting mechanism; A lifting control relief valve configured to ensure that the oil pressure in the lifting system (6) does not exceed a safe working pressure; and The material lifting system pressure sensor is integrated in the material lifting control valve group (61) to measure the oil pressure in the material lifting system (6).

7. The mobile box servo proportional system according to claim 1 or 2, wherein: The drive system (2) comprises: a motor operatively connected to the oil pump (3) to provide power to the oil pump (3); and a motor controller operably connected to the motor and configured to regulate the speed and direction of rotation of the motor; The motor controller adjusts the rotation speed of the motor based on the oil pressure in the push head system (5) and the lifting system (6).

8. The mobile box servo proportional system according to claim 1 or 2, wherein: The moving box servo proportional system includes two oil pumps (3).

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