Hydraulic control system and control method of garbage compression truck

Abstract

The embodiment of the present application provides a kind of garbage compression truck hydraulic control system and control method, it is related to garbage truck technical field.The hydraulic control system provided by the present application includes oil tank;Duplex pump has large flow oil outlet and small flow oil outlet;Compression circuit is fluidly connected between large flow oil outlet and the oil tank;Feeding circuit is fluidly connected between small flow oil outlet and oil tank;Confluence circuit is fluidly connected between compression circuit and feeding circuit;Multi-way valve has large flow joint and small flow joint, large flow joint is used to control the on-off of compression circuit, small flow joint is used to control the on-off of feeding circuit, and is used to control the excess flow of feeding circuit to compression circuit when the load of small flow joint is lower than the load of large flow joint;And when the pressure of small flow joint is higher than the pressure of large flow joint, compression circuit and feeding circuit are controlled to work independently.The present application can improve the problem that the energy consumption loss of current garbage compression truck hydraulic system is large.

Description

Technical Field

[0001] This invention relates to the field of garbage truck technology, and more specifically, to a hydraulic control system and control method for a garbage compactor truck. Background Technology

[0002] A garbage compactor truck is a specialized sanitation vehicle capable of collecting, compressing, transporting, and unloading garbage. Through its built-in compression mechanism, it compacts household waste, greatly increasing the loading capacity per trip and achieving efficient and sealed garbage transfer.

[0003] The inventors discovered that the hydraulic systems of current garbage compactors typically use a fixed-displacement pump and a switchable multi-way valve, which results in significant energy loss. Summary of the Invention

[0004] The present invention aims to provide a hydraulic control system and method for garbage compactors, which can improve the problem of high energy loss in the current hydraulic systems of garbage compactors.

[0005] The embodiments of the present invention can be implemented as follows: In a first aspect, the present invention provides a hydraulic control system for a garbage compactor truck, comprising: tank; A dual pump, fluidly connected to the oil tank, has a high-flow-rate oil outlet and a low-flow-rate oil outlet; A compression circuit is fluidly connected between the high-flow-rate oil outlet and the oil tank. The compression circuit includes a sliding plate cylinder and a scraper cylinder connected in parallel. The feeding circuit is fluidly connected between the low-flow oil outlet and the oil tank, and the feeding circuit includes a drum-tilting cylinder; A confluence circuit, in which fluid is connected between the compression circuit and the feeding circuit; A multi-way valve, fluidly connected to the dual pump, has a high-flow-rate connection and a low-flow-rate connection. The high-flow-rate connection controls the on / off state of the compression circuit, and the low-flow-rate connection controls the on / off state of the feeding circuit. Furthermore, the multi-way valve is used to control the excess flow from the feeding circuit to be combined with the compression circuit when the load pressure of the low-flow-rate connection is less than the load pressure of the high-flow-rate connection, and to control the compression circuit and the feeding circuit to operate independently when the load pressure of the low-flow-rate connection is greater than or equal to the load pressure of the high-flow-rate connection.

[0006] In an optional embodiment, the merging circuit includes a merging valve, which is fluidly connected between the high-flow-rate connection and the low-flow-rate connection. The merging valve has a first working position and a second working position. When the merging valve is in the first working position, the feeding circuit is unidirectionally connected to the compression circuit. When the merging valve is in the second working position, the feeding circuit is disconnected from the compression circuit. The confluence valve has a first end and a second end, the first end of which is fluidly connected to the compression circuit, and the second end of which is fluidly connected to the feeding circuit. When the merging valve is in the first working position, the merging valve is unidirectionally open from the second end to the first end; when the merging valve is in the second working position, the first end and the second end of the merging valve are closed.

[0007] In an optional embodiment, the merging circuit further includes a control valve, which is fluidly connected to the merging valve. The control valve is used to control the merging valve to be in a first working position when the load pressure of the compression circuit is greater than the load pressure of the feeding circuit; and to control the merging valve to be in a second working position when the load pressure of the compression circuit is less than or equal to the load pressure of the feeding circuit.

[0008] In an optional embodiment, the confluence valve has a valve core and a spring, the spring being disposed at a first end of the valve core.

[0009] The control valve includes a shuttle valve, which has a first oil port, a second oil port and a neutral oil port. The first oil port is fluidly connected to the compression circuit, the second oil port is fluidly connected to the feeding circuit, and the second oil port is fluidly connected to the first end of the valve core of the confluence valve. The neutral oil port is fluidly connected to the second end of the valve core of the confluence valve. The shuttle valve has a first working position and a second working position. When the load pressure of the compression circuit is greater than the load pressure of the feeding circuit, the first oil port is connected to the intermediate oil port, and the shuttle valve is located in the first working position. The compression circuit is connected to the second end of the confluence valve core, and the oil pressure at the second end of the confluence valve core is greater than the oil pressure at the first end. The confluence valve is located in the first working position. When the load pressure of the compression circuit is less than or equal to the load pressure of the feeding circuit, the second oil port is connected to the intermediate oil port, and the shuttle valve is located in the second working position. The feeding circuit is simultaneously connected to both the first and second ends of the confluence valve core, and the oil pressure at the first end of the confluence valve core is equal to the oil pressure at the second end. The confluence valve is located in the second working position under the action of a spring.

[0010] In an optional embodiment, a damping device is provided between the intermediate oil port and the second end of the valve core of the confluence valve.

[0011] In an optional embodiment, the multi-way valve is an electro-hydraulic proportional multi-way valve, which further includes a first electro-hydraulic proportional valve, a second electro-hydraulic proportional valve, and a third electro-hydraulic proportional valve. The first electro-hydraulic proportional valve is fluidly connected between the slide plate cylinder and the dual pump to control the extension or retraction of the slide plate cylinder and to control the flow rate of the slide plate cylinder. The second electro-hydraulic proportional valve is fluidly connected between the scraper cylinder and the dual pump to control the extension or retraction of the scraper cylinder and to control the flow rate of the scraper cylinder. The third electro-hydraulic proportional valve is fluidly connected between the tipping cylinder and the dual pump to control the extension or retraction of the tipping cylinder and to control the flow rate of the tipping cylinder.

[0012] In an optional embodiment, the merging circuit further includes a connecting oil circuit for connecting the first electro-hydraulic proportional valve, the second electro-hydraulic proportional valve, and the third electro-hydraulic proportional valve.

[0013] In an optional embodiment, the hydraulic control system further includes a position sensor and a controller. The position sensor is installed on the slide plate cylinder, the scraper cylinder, and the tipping cylinder. The position sensor is used to detect the position of the piston rod in the slide plate cylinder, the scraper cylinder, and the tipping cylinder and output a position signal. The controller is electrically connected to the position sensor, the first electro-hydraulic proportional valve, the second electro-hydraulic proportional valve, and the third electro-hydraulic proportional valve. The controller is used to receive the position signal and adjust the opening degree of the first electro-hydraulic proportional valve, the second electro-hydraulic proportional valve, and the third electro-hydraulic proportional valve according to the position signal.

[0014] Secondly, the present invention provides a hydraulic control method for a garbage compactor truck, used to control the hydraulic control system of the garbage compactor truck as described in any of the foregoing embodiments. The hydraulic control system has a first working condition, a second working condition, and a third working condition. In the first working condition, the tipping cylinder is activated, and the sliding plate cylinder and the scraper cylinder are stopped. In the second working condition, the sliding plate cylinder and the scraper cylinder are activated, and the tipping cylinder is stopped. In the third working condition, the sliding plate cylinder, the scraper cylinder, and the tipping cylinder are activated. The multi-way valve further includes a first electro-hydraulic proportional valve, a second electro-hydraulic proportional valve and a third electro-hydraulic proportional valve. The first electro-hydraulic proportional valve is used to control the extension or retraction of the slide plate cylinder, the second electro-hydraulic proportional valve is used to control the extension or retraction of the scraper cylinder, and the third electro-hydraulic proportional valve is used to control the extension or retraction of the tipping cylinder. The control method includes the following steps: In the second operating condition, the opening of the second electro-hydraulic proportional valve is adjusted to control the piston rod of the scraper cylinder to retract rapidly within a first set time. After the first set time, the piston rod of the scraper cylinder is controlled to retract at a constant speed. When the piston rod of the scraper cylinder retracts to the first set position, the opening of the second electro-hydraulic proportional valve is adjusted to control the piston rod of the scraper cylinder to decelerate to complete retraction within a second set time. The opening of the first electro-hydraulic proportional valve is adjusted to control the piston rod of the slide plate cylinder to extend rapidly within a second set time. After the second set time, the opening of the first electro-hydraulic proportional valve is adjusted to control the piston rod of the slide plate cylinder to extend at a constant speed. When the piston rod of the slide plate cylinder extends to the second set position, the opening of the first electro-hydraulic proportional valve is adjusted to control the piston rod of the slide plate cylinder to decelerate to fully extend within a third set time, and the opening of the second electro-hydraulic proportional valve is adjusted to control the piston rod of the scraper cylinder to accelerate extension within a third set time. After the third set time, the opening of the second electro-hydraulic proportional valve is adjusted to control the piston rod of the scraper cylinder to extend at a uniform speed. When the piston rod of the scraper cylinder extends to the third set position, the opening of the second electro-hydraulic proportional valve is adjusted to control the piston rod of the scraper cylinder to decelerate to fully extend within a fourth set time. The opening of the first electro-hydraulic proportional valve is adjusted to control the piston rod of the slide plate cylinder to accelerate retraction within a fourth set time. After the fourth set time, the opening of the first electro-hydraulic proportional valve is adjusted to control the piston rod of the slide plate cylinder to retract at a uniform speed. When the piston rod of the slide plate cylinder retracts to the fourth preset position, the opening of the first electro-hydraulic proportional valve is adjusted to control the piston rod of the slide plate cylinder to decelerate to fully retract within a first preset time, and the opening of the second electro-hydraulic proportional valve is adjusted to control the piston rod of the scraper cylinder to accelerate retraction within a first time.

[0015] In an optional implementation, the hydraulic control method further includes the following steps: Under the first working condition, the piston rod of the tipping cylinder is controlled to extend rapidly within a second set time period; After the tipping cylinder is fully extended, the piston rod of the tipping cylinder is controlled to accelerate and retract within a second set time. When the piston rod of the tipping cylinder retracts to the fourth set position, the piston rod of the tipping cylinder is controlled to decelerate to the first set speed within a third set time.

[0016] In an optional implementation, the hydraulic control method further includes the following steps: When the pressure of the small flow rate load is less than the pressure of the large flow rate load, and the excess flow of the feeding circuit is combined into the compression circuit, the hydraulic control system switches to the third working condition, controls the opening of the third electro-hydraulic proportional valve to decrease, and controls the opening of the first electro-hydraulic proportional valve and the second electro-hydraulic proportional valve to increase.

[0017] The beneficial effects of the hydraulic control system and method for garbage compactors provided in this invention include: A confluence circuit is set up between the compression circuit and the feeding circuit. When the load pressure of the compression circuit is greater than the load pressure of the feeding circuit, the feeding circuit is unidirectionally connected to the compression circuit. This allows excess oil in the low-flow feeding circuit to be replenished to the high-flow compression circuit, improving the working efficiency of the compression circuit, reducing the unloading loss of the feeding circuit, and reducing energy consumption. When the load pressure of the feeding circuit is greater than the load pressure of the compression circuit, the feeding circuit is disconnected from the compression circuit, so that the feeding circuit can work independently. This allows the compression circuit to be unloaded at low pressure when it is not working, effectively reducing energy consumption. Reduce oil circuit shock to achieve noise reduction. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of the hydraulic control system of the garbage compactor provided in this embodiment; Figure 2 This is a schematic diagram of the structure of the control valve in the merging circuit provided in this embodiment when it is in the first working position; Figure 3 This is a schematic diagram of the structure of the control valve in the merging circuit provided in this embodiment when it is in the second working position.

[0020] Icons: 100-Oil tank; 200-Dual pump; 210-High flow oil outlet; 220-Low flow oil outlet; 300-Compression circuit; 310-Slide plate cylinder; 320-Scraper cylinder; 330-First electro-hydraulic proportional valve; 340-Second electro-hydraulic proportional valve; 400-Feeding circuit; 410-Tilting cylinder; 420-Third electro-hydraulic proportional valve; 500-Merging circuit; 510-Merging valve; 520-Control valve; 530-Damping; 540-Connecting oil circuit; a-First oil port; b-Second oil port; c-Neutral oil port. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0022] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0023] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0024] In the description of this invention, it should be noted that if terms such as "upper," "lower," "inner," or "outer" are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship in which the product of this invention is usually placed, they are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0025] Furthermore, the terms "first" and "second" are used only to distinguish descriptions and should not be interpreted as indicating or implying relative importance.

[0026] It should be noted that, where there is no conflict, the features in the embodiments of the present invention can be combined with each other.

[0027] A garbage compactor truck is a specialized sanitation vehicle capable of collecting, compressing, transferring, and unloading garbage. Through its built-in compression mechanism, it compacts household waste, significantly increasing the loading capacity per trip and achieving efficient, sealed garbage transfer. The compactor truck's operating mechanism typically includes a loader, a compression mechanism, and a tipping mechanism. The loader is located at the unloading port at the rear of the garbage bin for loading garbage. The compression mechanism compresses the garbage and loads it into the garbage bin, while the tipping mechanism empties the garbage from the bin into the loader.

[0028] Currently, the hydraulic systems of garbage compactors generally include the following three schemes: variable displacement pump with load-sensitive electro-hydraulic proportional valve, fixed displacement pump with load-sensitive electro-hydraulic proportional valve, and fixed displacement pump with electro-hydraulic on / off valve. Among them, the scheme using a fixed displacement pump with a load-sensitive electro-hydraulic proportional valve has the following problems when using a dual pump: when only the compression circuit is working, the full flow of the feeding circuit needs to be unloaded; when the compression and feeding circuits are operating simultaneously, the excess flow of the feeding speed regulation needs to be unloaded, resulting in energy loss. When using a single pump, a relatively high pump displacement and valve diameter are required to ensure efficiency. When only the feeding circuit is operating, the compression circuit needs to be unloaded according to the load pressure of the feeding circuit, resulting in significant energy loss.

[0029] Furthermore, the solution using a variable displacement pump with a load-sensitive electro-hydraulic proportional valve is limited in its adoption in the domestic sanitation sector due to the variable displacement pump's poor pollution resistance and high cost. The solution using a fixed displacement pump with an electro-hydraulic switching valve cannot achieve real-time, precise speed control of the hydraulic actuators, resulting in large hydraulic shocks, significant throttling heat generation, and high energy consumption; moreover, simultaneous operation within the same circuit is impossible.

[0030] To address the aforementioned technical problems, this invention provides a hydraulic control system and method for a garbage compactor truck. The following detailed description, through embodiments and in conjunction with the accompanying drawings, outlines the overall structure, working principle, and technical effects of the hydraulic control system provided by this invention, as well as the detailed steps, implementation principles, and technical effects of the supporting hydraulic method.

[0031] Please refer to Figures 1-3 This invention provides a hydraulic control system for a garbage compactor truck, which is applied to the garbage compactor truck to control the operation of the compaction mechanism and the tipping mechanism of the garbage compactor truck, and to improve the problem of high energy consumption of the current hydraulic system of garbage compactor truck.

[0032] Please refer to Figure 1The hydraulic control system for a garbage compactor truck provided by this invention includes an oil tank 100, a dual pump 200, a compression circuit 300, a feeding circuit 400, a confluence circuit 500, and a multi-way valve. The dual pump 200 is fluidly connected to the oil tank 100 and is a dual gear pump with a large-flow outlet 210 and a small-flow outlet 220. The compression circuit 300 is fluidly connected between the large-flow outlet 210 of the dual pump 200 and the oil tank 100, and includes a sliding plate cylinder 310 and a scraper cylinder 320 connected in parallel. The feeding circuit 400 is fluidly connected between the small-flow outlet 220 and the oil tank 100, and includes a tipping cylinder 410 fluidly connected to the small-flow outlet 220 of the dual pump 200. The confluence circuit 500 is fluidly connected between the compression circuit 300 and the feeding circuit 400. A multi-way valve is fluidly connected to the dual pump 200. The multi-way valve has a high-flow-rate connection and a low-flow-rate connection. The high-flow-rate connection is used to control the on / off state of the compression circuit 300, and the low-flow-rate connection is used to control the on / off state of the feeding circuit 400. Furthermore, the multi-way valve is used to control the excess flow from the feeding circuit 400 to be combined with the compression circuit 300 when the load pressure of the low-flow-rate connection is less than the load pressure of the high-flow-rate connection, and to control the compression circuit 300 and the feeding circuit 400 to operate independently when the load pressure of the low-flow-rate connection is greater than or equal to the load pressure of the high-flow-rate connection.

[0033] By setting up a confluence circuit 500 connecting the compression circuit 300 and the feeding circuit 400, when both the compression circuit 300 and the feeding circuit 400 are working simultaneously, and the load pressure of the compression circuit 300 is greater than the load pressure of the feeding circuit 400, the feeding circuit 400 is unidirectionally connected to the compression circuit 300. This allows excess oil in the low-flow feeding circuit 400 to replenish the high-flow compression circuit 300, improving the working efficiency of the compression circuit 300 and reducing the unloading loss of the feeding circuit 400, thus reducing energy consumption. Conversely, when the load pressure of the feeding circuit 400 is greater than or equal to the load pressure of the compression circuit 300, the feeding circuit 400 is disconnected from the compression circuit 300, allowing the feeding circuit 400 to work independently. This enables low-pressure unloading when the compression circuit 300 is not working, effectively reducing energy consumption. This improves the high energy consumption problem of the current hydraulic control system of garbage compactors, enhancing the high efficiency and energy-saving performance of garbage compactors.

[0034] Understandably, the slide plate cylinder 310 is connected to the slide plate to drive it upwards or downwards. When the piston rod of the slide plate cylinder 310 retracts, the slide plate moves upwards and compresses the garbage; when the piston rod of the slide plate cylinder 310 extends, the slide plate moves downwards to reset and crush the garbage. The scraper cylinder 320 is connected to the scraper to drive the slide plate to open or close. When the piston rod of the scraper cylinder 320 extends, the scraper closes to compress and grab the garbage; when the piston rod of the scraper cylinder 320 retracts, the scraper opens to reset. The tipping cylinder 410 is connected to the bin-hanging frame to drive the bin-hanging frame to lift or lower. The bin-hanging frame carries the garbage bin. When the piston rod of the tipping cylinder 410 extends, it drives the garbage bin to lift and tip the garbage inside into the garbage truck; when the piston rod of the tipping cylinder 410 retracts, it drives the garbage bin to lower and returns the empty garbage bin to the ground.

[0035] Please refer to Figures 1-3 In some optional embodiments, the merging circuit 500 includes a merging valve 510, which is fluidly connected between the high-flow-rate connection and the low-flow-rate connection. The merging valve 510 has a first operating position and a second operating position. When the merging valve 510 is in the first operating position, the feeding circuit 400 is unidirectionally connected to the compression circuit 300; when the merging valve 510 is in the second operating position, the feeding circuit 400 is disconnected from the compression circuit 300. Further, the merging valve 510 has opposing first and second ends. The first end of the merging valve 510 is fluidly connected to the compression circuit 300, and the second end of the merging valve 510 is fluidly connected to the feeding circuit 400. When the merging valve 510 is in the first operating position, it unidirectionally flows from the second end to the first end; when the merging valve 510 is in the second operating position, the first and second ends of the merging valve 510 are cut off. By controlling the confluence valve 510 to switch between the first working position and the second working position, the feeding circuit 400 is controlled to replenish oil to the compression circuit 300, and the feeding circuit 400 and the compression circuit 300 are controlled to operate independently.

[0036] Please refer to Figure 2 and Figure 3 In some optional embodiments, the merging circuit 500 further includes a control valve 520, which is fluidly connected to the merging valve 510. The control valve 520 is used to control the merging valve 510 to a first working position when the load pressure of the compression circuit 300 is greater than the load pressure of the feeding circuit 400; and to control the merging valve 510 to a second working position when the load pressure of the compression circuit 300 is less than or equal to the load pressure of the feeding circuit 400. The control valve 520 is used to control the merging valve 510 to switch between the first and second working positions.

[0037] Specifically, please refer to Figure 2 and Figure 3In some alternative embodiments, the confluence valve 510 has a valve core and a spring, with the spring disposed at the first end of the valve core. Initially, the confluence valve 510 is always in a closed state under the action of the spring. The control valve 520 includes a shuttle valve having a first port a, a second port b, and a neutral port c, with the first port a and the second port b positioned opposite each other. The first port a is fluidly connected to the compression circuit 300, and the second port b is fluidly connected to the feeding circuit 400. Further, the second port b is fluidly connected to the first end of the valve core of the confluence valve 510, and the neutral port c is fluidly connected to the second end of the valve core of the confluence valve 510.

[0038] Furthermore, the valve core of the shuttle valve always blocks either the first oil port a or the second oil port b, giving the shuttle valve a first working position and a second working position. When the load pressure of the compression circuit 300 is greater than the load pressure of the feeding circuit 400, the first oil port a is connected to the neutral oil port c, and the shuttle valve is in the first working position. At this time, the compression circuit 300 is connected to the second end of the valve core of the confluence valve 510. The oil pressure at the second end of the valve core of the confluence valve 510 is equal to the load pressure of the compression circuit 300, while the oil pressure at the first end of the valve core of the confluence valve 510 is the same as the load pressure of the feeding circuit 400, making the oil pressure at the second end of the valve core of the confluence valve 510 greater than the oil pressure at the first end, and the confluence valve 510 is in the first working position. At this time, the second end of the confluence valve 510 is unidirectionally connected to the first end, so that the feeding circuit 400 can replenish oil to the compression circuit 300.

[0039] When the load pressure of the compression circuit 300 is less than the load pressure of the feeding circuit 400, the valve core of the shuttle valve moves to block the first oil port a under the action of the oil pressure difference, and the second oil port b of the shuttle valve is connected to the neutral oil port c, and the shuttle valve is in the second working position. At this time, the feeding circuit 400 is simultaneously connected to the first end and the second end of the valve core of the confluence valve 510. The oil pressure at the first end of the valve core of the confluence valve 510 is equal to the oil pressure at the second end, and the confluence valve 510 is in the second working position under the action of the spring. At this time, the confluence valve 510 is closed, and the feeding circuit 400 and the compression circuit 300 work independently.

[0040] Furthermore, a damper 530 is provided between the intermediate oil port c and the second end of the valve core of the confluence valve 510 to limit the flow rate of oil from the intermediate oil port to the second end of the valve core of the confluence valve 510.

[0041] Please refer to Figure 1In some optional embodiments, a multi-way electro-hydraulic proportional valve is provided. The multi-way valve further includes a first electro-hydraulic proportional valve 330, a second electro-hydraulic proportional valve 340, and a third electro-hydraulic proportional valve 420. The first electro-hydraulic proportional valve 330 is fluidly connected between the slide block cylinder 310 and the dual pump 200. The first electro-hydraulic proportional valve 330 controls the communication between the dual pump 200 and the rod-side or rodless-side chamber of the slide block cylinder 310, thereby controlling the extension or retraction of the slide block cylinder 310. Furthermore, the first electro-hydraulic proportional valve 330 can also control the flow rate of oil entering the slide block cylinder 310, thereby controlling the actuation speed of the piston rod of the slide block cylinder 310. The second electro-hydraulic proportional valve 340 is fluidly connected between the scraper cylinder 320 and the dual pump 200. The second electro-hydraulic proportional valve 340 controls the communication between the dual pump 200 and the rod-side or rodless-side chamber of the scraper cylinder 320, thereby controlling the extension or retraction of the scraper cylinder 320. Furthermore, the second electro-hydraulic proportional valve 340 is also used to control the flow rate of oil entering the scraper cylinder 320, thereby controlling the operating speed of the piston rod of the slide block cylinder 310. The third electro-hydraulic proportional valve 420 is fluidly connected between the tipping cylinder 410 and the dual pump 200. The third electro-hydraulic proportional valve 420 is used to control the communication between the dual pump 200 and the rod-side or rodless-side chamber of the tipping cylinder 410, thereby controlling the extension or retraction of the tipping cylinder 410. Furthermore, the third electro-hydraulic proportional valve 420 can also control the flow rate of oil input from the dual pump 200 to the tipping cylinder 410, thereby controlling the operating speed of the piston rod of the tipping cylinder 410.

[0042] Please refer to Figures 1-3 Furthermore, the confluence circuit also includes a connecting oil circuit 540. One end of the connecting oil circuit 540 is fluidly connected to the first electro-hydraulic proportional valve 330 and the second electro-hydraulic proportional valve 340 in the compression circuit 300, and the other end of the connecting oil circuit 540 is fluidly connected to the third electro-hydraulic proportional valve 420 in the feeding circuit 400. This connects the control oil in the compression circuit 300 and the feeding circuit 400 to facilitate the control of the operation of the first electro-hydraulic proportional valve 330, the second electro-hydraulic proportional valve 340, and the third electro-hydraulic proportional valve 420.

[0043] In some optional embodiments, the hydraulic control system of the garbage compactor truck also includes position sensors and a controller. Position sensors are installed on the sliding plate cylinder 310, scraper cylinder 320, and tipping cylinder 410. The position sensors detect the position of the piston rods in these cylinders and output position signals. The controller is electrically connected to the position sensors, the first electro-hydraulic proportional valve 330, the second electro-hydraulic proportional valve 340, and the third electro-hydraulic proportional valve 420. The controller receives the position signals output by the position sensors and adjusts the opening degrees of the first electro-hydraulic proportional valve 330, the second electro-hydraulic proportional valve 340, and the third electro-hydraulic proportional valve 420 according to the position signals, thereby controlling the operating speed of the sliding plate cylinder 310, the scraper cylinder 320, and the tipping cylinder 410.

[0044] In summary, the implementation principle of the hydraulic control system for garbage compactors provided by this invention is as follows: A confluence circuit 500 is set up between the compression circuit 300 and the feeding circuit 400. When the compression circuit 300 and the feeding circuit 400 are working simultaneously, and the load pressure of the compression circuit 300 is greater than the load pressure of the feeding circuit 400, the feeding circuit 400 is unidirectionally connected to the compression circuit 300. This allows excess oil in the low-flow feeding circuit 400 to replenish the high-flow compression circuit 300, improving the working efficiency of the compression circuit 300 and reducing the unloading loss of the feeding circuit 400, thus reducing energy consumption. Conversely, when the load pressure of the feeding circuit 400 is greater than the load pressure of the compression circuit 300, the feeding circuit 400 is disconnected from the compression circuit 300, allowing the feeding circuit 400 to work independently. This enables low-pressure unloading when the compression circuit 300 is not working, effectively reducing energy consumption. This improves the high energy consumption problem of current hydraulic control systems for garbage compactors and enhances the high efficiency and energy-saving performance of garbage compactors.

[0045] The present invention also provides a hydraulic control method for a garbage compactor truck, used to control the hydraulic control system of the garbage compactor truck provided in any of the above optional embodiments. The garbage truck hydraulic control system has a first working condition, a second working condition, and a third working condition. In the first working condition, the tipping cylinder 410 is activated, while the sliding plate cylinder 310 and the scraper cylinder 320 are stopped. In the second working condition, the sliding plate cylinder 310 and the scraper cylinder 320 are activated, while the tipping cylinder 410 is stopped. In the third working condition, the sliding plate cylinder 310, the scraper cylinder 320, and the tipping cylinder 410 are activated.

[0046] Specifically, the hydraulic control method for garbage compactors includes the following steps: In step S100, under the second working condition, the opening of the second electro-hydraulic proportional valve 340 is adjusted to control the piston rod of the scraper cylinder 320 to retract rapidly within a first set time. After the first set time, the piston rod of the scraper cylinder 320 is controlled to retract at a constant speed. When the piston rod of the scraper cylinder 320 retracts to the first set position, the opening of the second electro-hydraulic proportional valve 340 is adjusted to control the piston rod of the scraper cylinder 320 to decelerate to fully retract within the first set time. The opening of the first electro-hydraulic proportional valve 330 is adjusted to control the piston rod of the slide plate cylinder 310 to extend rapidly within a second set time. After the second set time, the opening of the first electro-hydraulic proportional valve 330 is adjusted to control the piston rod of the slide plate cylinder 310 to extend at a constant speed.

[0047] Specifically, in the second operating condition, when the tipping cylinder 410 stops and the sliding plate cylinder 310 and scraper cylinder 320 operate to compress waste, the outlet of the second electro-hydraulic proportional valve 340 is connected to the rod chamber of the scraper cylinder 320. The second electro-hydraulic proportional valve 340 gradually opens to full open within a first set time, causing the piston rod of the scraper cylinder 320 to retract rapidly within the first set time, and the scraper performs an opening action. When the piston rod of the scraper cylinder 320 moves to a first set position and is sensed by the position sensor, the controller controls the second electro-hydraulic proportional valve 340 to gradually close within a second set time; and controls the first electro-hydraulic proportional valve 330 to gradually open to full open within a second set time, to control the piston rod of the sliding plate cylinder 310 to extend rapidly within the second set time. The piston rod of the scraper cylinder 320 decelerates and retracts until it is fully retracted within the second set time, at which point the scraper is fully open.

[0048] In step S200, when the piston rod of the slide plate cylinder 310 extends to the second set position, the opening of the first electro-hydraulic proportional valve 330 is adjusted to control the piston rod of the slide plate cylinder 310 to decelerate to fully extend within a third set time. The opening of the second electro-hydraulic proportional valve 340 is adjusted to control the piston rod of the scraper cylinder 320 to accelerate its extension within a third set time. After the third set time, the opening of the second electro-hydraulic proportional valve 340 is adjusted to control the piston rod of the scraper cylinder 320 to extend at a uniform speed.

[0049] Specifically, when the piston rod of the slide plate cylinder 310 moves to the second preset position and is sensed by the position sensor, the controller controls the first electro-hydraulic proportional valve 330 to gradually close within a third preset time period, thereby controlling the piston rod of the slide plate cylinder 310 to decelerate and extend within the third preset time period until it is fully extended, and the slide plate descends to its position. Simultaneously, the controller controls the second electro-hydraulic proportional valve 340, which is connected to the rodless chamber of the scraper cylinder 320, to gradually open to a fully open state within the third preset time period, thereby controlling the piston rod of the scraper cylinder 320 to accelerate its extension within the third preset time period, and the scraper performs the scraping action.

[0050] In step S300, when the piston rod of the scraper cylinder 320 extends to the third set position, the opening of the second electro-hydraulic proportional valve 340 is adjusted to control the piston rod of the scraper cylinder 320 to decelerate to fully extend within a fourth set time. The opening of the first electro-hydraulic proportional valve 330 is adjusted to control the piston rod of the slide plate cylinder 310 to accelerate retraction within a fourth set time. After the fourth set time, the opening of the first electro-hydraulic proportional valve 330 is adjusted to control the piston rod of the slide plate cylinder 310 to retract at a uniform speed.

[0051] Specifically, when the piston rod of the scraper cylinder 320 extends to the third preset position and is detected by the position sensor, the controller controls the second electro-hydraulic proportional valve 340 to gradually close within a fourth preset time period, thereby controlling the piston rod of the scraper cylinder 320 to decelerate its extension within the fourth preset time period until it is fully extended. Simultaneously, the controller controls the first electro-hydraulic proportional valve 330 to gradually open to the fully open state within the fourth preset time period, thereby driving the piston rod of the slide plate cylinder 310 to accelerate its retraction within the fourth preset time period.

[0052] In step S400, when the piston rod of the slide plate cylinder 310 retracts to the fourth set position, the opening of the first electro-hydraulic proportional valve 330 is adjusted to control the piston rod of the slide plate cylinder 310 to decelerate to fully retract within a first set time, and the opening of the second electro-hydraulic proportional valve 340 is adjusted to control the piston rod of the scraper cylinder 320 to accelerate retraction within a first time.

[0053] Furthermore, when the piston rod of the slide cylinder 310 moves to the fourth position and is sensed by the position sensor, the controller controls the first electro-hydraulic proportional valve 330 to gradually close within a first set time, driving the piston rod of the slide cylinder 310 to decelerate and retract within the first set time until it is fully retracted.

[0054] Thus, when the slide plate cylinder 310 and the scraper cylinder 320 are activated, they both accelerate to start and decelerate to stop. At the same time as the first electro-hydraulic proportional valve 330 reduces its opening, the second electro-hydraulic proportional valve 340 increases its opening; or at the same time as the first electro-hydraulic proportional valve 330 increases its opening, the second electro-hydraulic proportional valve 340 decreases its opening. This maintains a relatively constant total demand flow of the compression circuit 300, reduces the overflow of excess flow, and achieves the effect of reducing energy consumption.

[0055] In some optional embodiments, the hydraulic control method for garbage compactors provided by the present invention further includes the following steps: Under the first operating condition, the piston rod of the control cylinder 410 extends rapidly within a second set time period; After the piston rod of the tipping cylinder 410 is fully extended, the piston rod of the tipping cylinder 410 is controlled to accelerate and retract within a second set time. When the piston rod of the tipping cylinder 410 retracts to the fourth set position, the piston rod of the tipping cylinder 410 is controlled to decelerate to the first set speed within a third set time.

[0056] Specifically, in the first operating condition, i.e., when only the feeding circuit 400 is working, the controller controls the third electro-hydraulic proportional valve 420 to gradually open within a second set time, thereby controlling the piston rod of the tipping cylinder 410 to extend rapidly within the second set time, driving the garbage bin to move at high speed to ensure that the garbage is emptied cleanly. After the piston rod of the tipping cylinder 410 is fully extended, the controller controls the third electro-hydraulic proportional valve 420 to gradually close within the second set time, thereby controlling the piston rod of the tipping cylinder 410 to retract rapidly within the second set time. When the piston rod of the tipping cylinder 410 retracts to the fourth set position and is sensed by the position sensor, the controller controls the third electro-hydraulic proportional valve 420 to gradually close within a third set time, causing the piston rod of the tipping cylinder 410 to decelerate to the first set speed within the third set time, driving the garbage bin to descend smoothly to ensure stable placement of the bin.

[0057] In some optional embodiments, the hydraulic control method for garbage compactors provided by the present invention further includes the following steps: When the pressure of the small flow load is less than that of the large flow load, and the excess flow of the feeding circuit 400 is combined into the compression circuit 300, the hydraulic control system switches to the third working condition, controls the opening of the third electro-hydraulic proportional valve 420 to decrease, and controls the opening of the first electro-hydraulic proportional valve 330 and the second electro-hydraulic proportional valve 340 to increase.

[0058] Specifically, when the piston rod of the tipping cylinder 410 is retracted by the feeding circuit 400, the load direction of the feeding circuit 400 and the movement direction of the tipping cylinder 410 are consistent. At this time, as long as the compression circuit 300 is in working state, the confluence condition is met. To avoid the impact caused by the excessively fast feeding reset speed, the opening of the third electro-hydraulic proportional valve 420 in the feeding circuit 400 needs to be reduced to reduce the flow rate of the feeding circuit 400. The excess flow rate is then combined with the compression circuit 300 through the confluence valve 510. Correspondingly, according to different working conditions, the opening of the first electro-hydraulic proportional valve 330 and / or the second electro-hydraulic proportional valve 340 is increased to increase the speed of the slide plate cylinder 310 and / or the scraper cylinder 320.

[0059] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in the present invention should be included within the scope of protection of the present invention.

Claims

1. A hydraulic control system for a garbage compactor truck, characterized in that, include: Fuel tank (100); A dual pump (200) is fluidly connected to the oil tank (100) and has a high-flow-rate oil outlet (210) and a low-flow-rate oil outlet (220); a compression circuit (300) is fluidly connected between the high-flow-rate oil outlet (210) and the oil tank (100), and the compression circuit (300) includes a sliding plate cylinder (310) and a scraper cylinder (320) arranged in parallel. The feeding circuit (400) is fluidly connected between the low-flow oil outlet (220) and the oil tank (100), and the feeding circuit (400) includes a tilting cylinder (410). A merging circuit (500) is fluidly connected between the compression circuit (300) and the feeding circuit (400); A multi-way valve is fluidly connected to the dual pump (200). The multi-way valve has a high-flow-rate connection and a low-flow-rate connection. The high-flow-rate connection is used to control the on / off state of the compression circuit (300), and the low-flow-rate connection is used to control the on / off state of the feeding circuit (400). Furthermore, the multi-way valve is used to control the excess flow of the feeding circuit (400) to be combined with the compression circuit (300) when the load pressure of the low-flow-rate connection is less than the load pressure of the high-flow-rate connection, and to control the compression circuit (300) and the feeding circuit (400) to operate independently when the load pressure of the low-flow-rate connection is greater than or equal to the load pressure of the high-flow-rate connection.

2. The hydraulic control system for the garbage compactor truck according to claim 1, characterized in that, The merging circuit (500) includes a merging valve (510), which is fluidly connected between the high-flow-rate connection and the low-flow-rate connection. The merging valve (510) has a first working position and a second working position. When the merging valve (510) is in the first working position, the feeding circuit (400) is unidirectionally connected to the compression circuit (300). When the merging valve (510) is in the second working position, the feeding circuit (400) is disconnected from the compression circuit (300). The confluence valve (510) has a first end and a second end opposite to each other. The first end of the confluence valve (510) is fluidly connected to the compression circuit (300), and the second end of the confluence valve (510) is fluidly connected to the feeding circuit (400). When the merging valve (510) is in the first working position, the merging valve (510) is unidirectionally open from the second end to the first end; when the merging valve (510) is in the second working position, the first end and the second end of the merging valve (510) are cut off.

3. The hydraulic control system for the garbage compactor truck according to claim 2, characterized in that, The merging circuit (500) further includes a control valve (520), which is fluidly connected to the merging valve (510). The control valve (520) is used to control the merging valve (510) to be in a first working position when the load pressure of the compression circuit (300) is greater than the load pressure of the feeding circuit (400); and to control the merging valve (510) to be in a second working position when the load pressure of the compression circuit (300) is less than or equal to the load pressure of the feeding circuit (400).

4. The hydraulic control system for the garbage compactor truck according to claim 3, characterized in that, The confluence valve (510) has a valve core and a spring, the spring being disposed at the first end of the valve core; The control valve (520) includes a shuttle valve having a first port (a), a second port (b), and a neutral port (c). The first port (a) is fluidly connected to the compression circuit (300), the second port (b) is fluidly connected to the feeding circuit (400), and the second port (b) is fluidly connected to the first end of the valve core of the confluence valve (510). The neutral port (c) is fluidly connected to the second end of the valve core of the confluence valve (510). The shuttle valve has a first working position and a second working position. When the load pressure of the compression circuit (300) is greater than the load pressure of the feeding circuit (400), the first oil port (a) is connected to the middle oil port (c), the shuttle valve is located in the first working position, the compression circuit (300) is connected to the second end of the valve core of the confluence valve (510), the oil pressure at the second end of the valve core of the confluence valve (510) is greater than the oil pressure at the first end, and the confluence valve (510) is located in the first working position. When the load pressure of the compression circuit (300) is less than or equal to the load pressure of the feeding circuit (400), the second oil port (b) is connected to the middle oil port (c), the shuttle valve is located in the second working position, the feeding circuit (400) is simultaneously connected to the first end and the second end of the valve core of the confluence valve (510), the oil pressure at the first end of the valve core of the confluence valve (510) is equal to the oil pressure at the second end, and the confluence valve (510) is located in the second working position under the action of the spring.

5. The hydraulic control system for the garbage compactor truck according to claim 4, characterized in that, A damper (530) is provided between the intermediate oil port (c) and the second end of the valve core of the confluence valve (510).

6. The hydraulic control system for the garbage compactor truck according to claim 1, characterized in that, The multi-way valve is an electro-hydraulic proportional multi-way valve, which further includes a first electro-hydraulic proportional valve (330), a second electro-hydraulic proportional valve (340), and a third electro-hydraulic proportional valve (420). The first electro-hydraulic proportional valve (330) is fluidly connected between the slide plate cylinder (310) and the dual pump (200) to control the extension or retraction of the slide plate cylinder (310) and to control the flow rate of the slide plate cylinder (310). The second electro-hydraulic proportional valve (340) is fluidly connected between the scraper cylinder (320) and the dual pump (200) to control the extension or retraction of the scraper cylinder (320) and to control the flow rate of the scraper cylinder (320). The third electro-hydraulic proportional valve (420) is fluidly connected between the tipping cylinder (410) and the dual pump (200) to control the extension or retraction of the tipping cylinder (410) and to control the flow rate of the tipping cylinder (410).

7. The hydraulic control system for the garbage compactor truck according to claim 6, characterized in that, The confluence circuit also includes a connecting oil circuit (540), which is used to connect the first electro-hydraulic proportional valve (330), the second electro-hydraulic proportional valve (340), and the third electro-hydraulic proportional valve (420).

8. The hydraulic control system for the garbage compactor truck according to claim 6, characterized in that, The hydraulic control system further includes a position sensor and a controller. The position sensor is installed on the slide plate cylinder (310), the scraper cylinder (320), and the tipping cylinder (410). The position sensor is used to detect the position of the piston rod in the slide plate cylinder (310), the scraper cylinder (320), and the tipping cylinder (410) and output a position signal. The controller is electrically connected to the position sensor, the first electro-hydraulic proportional valve (330), the second electro-hydraulic proportional valve (340), and the third electro-hydraulic proportional valve (420). The controller is used to receive the position signal and adjust the opening degree of the first electro-hydraulic proportional valve (330), the second electro-hydraulic proportional valve (340), and the third electro-hydraulic proportional valve (420) according to the position signal.

9. A hydraulic control method for a garbage compactor truck, used to control the hydraulic control system of the garbage compactor truck as described in any one of claims 1-8, characterized in that, The hydraulic control system has a first working condition, a second working condition, and a third working condition. In the first working condition, the tipping cylinder (410) is activated, and the sliding plate cylinder (310) and the scraper cylinder (320) are stopped. In the second working condition, the sliding plate cylinder (310) and the scraper cylinder (320) are activated, and the tipping cylinder (410) is stopped. In the third working condition, the sliding plate cylinder (310), the scraper cylinder (320), and the tipping cylinder (410) are activated. The multi-way valve also includes a first electro-hydraulic proportional valve (330), a second electro-hydraulic proportional valve (340), and a third electro-hydraulic proportional valve (420). The first electro-hydraulic proportional valve (330) is used to control the extension or retraction of the slide plate cylinder (310), the second electro-hydraulic proportional valve (340) is used to control the extension or retraction of the scraper cylinder (320), and the third electro-hydraulic proportional valve (420) is used to control the extension or retraction of the tipping cylinder (410). The control method includes the following steps: In the second working condition, the opening of the second electro-hydraulic proportional valve (340) is adjusted to control the piston rod of the scraper cylinder (320) to accelerate its retraction within a first set time. After the first set time, the piston rod of the scraper cylinder (320) is controlled to retract at a constant speed. When the piston rod of the scraper cylinder (320) retracts to the first set position, the opening of the second electro-hydraulic proportional valve (340) is adjusted to control the piston rod of the scraper cylinder (320) to decelerate to complete retraction within a second set time. The opening of the first electro-hydraulic proportional valve (330) is adjusted to control the piston rod of the slide plate cylinder (310) to accelerate its extension within a second set time. After the second set time, the opening of the first electro-hydraulic proportional valve (330) is adjusted to control the piston rod of the slide plate cylinder (310) to extend at a constant speed. When the piston rod of the slide plate cylinder (310) extends to the second set position, the opening of the first electro-hydraulic proportional valve (330) is adjusted to control the piston rod of the slide plate cylinder (310) to decelerate to fully extend within a third set time, and the opening of the second electro-hydraulic proportional valve (340) is adjusted to control the piston rod of the scraper cylinder (320) to accelerate extension within a third set time. After the third set time, the opening of the second electro-hydraulic proportional valve (340) is adjusted to control the piston rod of the scraper cylinder (320) to extend at a uniform speed. When the piston rod of the scraper cylinder (320) extends to the third set position, the opening of the second electro-hydraulic proportional valve (340) is adjusted to control the piston rod of the scraper cylinder (320) to decelerate to fully extend within a fourth set time. The opening of the first electro-hydraulic proportional valve (330) is adjusted to control the piston rod of the slide plate cylinder (310) to accelerate retraction within a fourth set time. After the fourth set time, the opening of the first electro-hydraulic proportional valve (330) is adjusted to control the piston rod of the slide plate cylinder (310) to retract at a uniform speed. When the piston rod of the slide plate cylinder (310) retracts to the fourth set position, the opening of the first electro-hydraulic proportional valve (330) is adjusted to control the piston rod of the slide plate cylinder (310) to decelerate to fully retract within a first set time, and the opening of the second electro-hydraulic proportional valve (340) is adjusted to control the piston rod of the scraper cylinder (320) to accelerate retraction within a first time.

10. The hydraulic control method for a garbage compactor truck according to claim 9, characterized in that, The hydraulic control method further includes the following steps: Under the first working condition, the piston rod of the tipping cylinder (410) is accelerated to extend within a second set time period; After the tipping cylinder (410) is fully extended, the piston rod of the tipping cylinder (410) is controlled to accelerate and retract within a second set time. When the piston rod of the tipping cylinder (410) retracts to the fourth set position, the piston rod of the tipping cylinder (410) is controlled to decelerate to the first set speed within a third set time.

11. The hydraulic control method for a garbage compactor truck according to claim 9, characterized in that, The hydraulic control method further includes the following steps: When the pressure of the small flow load is less than the pressure of the large flow load, and the excess flow of the feeding circuit (400) is combined into the compression circuit (300), the hydraulic control system switches to the third working condition, controls the opening of the third electro-hydraulic proportional valve (420) to decrease, and controls the opening of the first electro-hydraulic proportional valve (330) and the second electro-hydraulic proportional valve (340) to increase.

Images