Hydraulic control system of garbage compression truck and garbage compression truck
By designing a hydraulic control system suitable for garbage compactors, the system achieves universality between American and Japanese models, reduces purchase costs, solves the problem of poor universality of hydraulic systems in existing technologies, and expands the scope of application.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- ZOOMLION ENVIRONMENTAL IND CO LTD
- Filing Date
- 2025-08-25
- Publication Date
- 2026-07-21
AI Technical Summary
The existing hydraulic systems of garbage compactors have poor versatility and limited applicability due to differences between American and Japanese models, which increases the purchase cost.
Design a hydraulic control system for a garbage compactor truck. The system uses a dual pump and an adjusting component to switch between confluence and divergence states. It is applicable to two types of garbage compactors and includes an oil tank, a first cylinder group, a second cylinder group, a multi-way valve group, and an adjusting component. The adjusting component controls the connection and disconnection of the oil passages under different states to adapt to different working conditions.
This achieves good versatility for both types of garbage compactors, reduces the purchase cost of the hydraulic system, and improves the applicability and compatibility of the hydraulic system.
Smart Images
Figure CN224533103U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of garbage compactor truck technology, and more specifically, to a hydraulic control system for a garbage compactor truck and a garbage compactor truck. Background Technology
[0002] Garbage compactor trucks are specialized urban sanitation vehicles that efficiently collect and transport garbage, making a significant contribution to improving urban environmental sanitation. Their main moving parts include scrapers, sliding plates, pushers, fillers, and lifting mechanisms, all driven by a hydraulic system.
[0003] Currently, the industry generally offers two types of garbage compactor trucks to meet different customer needs: the first is the American-made compactor truck, which boasts large capacity and high efficiency in compaction cycle operations; the second is the environmentally friendly and economical Japanese-made compactor truck. Due to the different characteristics of these two types of garbage compactor trucks, their hydraulic system principles and control logic differ, resulting in poor versatility and limited applicability of the hydraulic systems. This hinders the standardization of garbage compactor truck hydraulic systems and the reduction of purchase costs. Utility Model Content
[0004] The purpose of this utility model is to provide a hydraulic control system for a garbage compactor and a garbage compactor, which can be applied to the two mainstream types of garbage compactors, has the advantage of good versatility, and can effectively reduce the purchase cost of the hydraulic system.
[0005] The embodiments of this utility model can be implemented as follows: In a first aspect, this utility model provides a hydraulic control system for a garbage compactor truck, including an oil tank, a first cylinder group, and a second cylinder group. The hydraulic control system further includes: A tandem pump, wherein the input end of the tandem pump is fluidly connected to the oil tank, and the tandem pump comprises a large pump and a small pump; The first multi-way valve group is fluidly connected to the first hydraulic cylinder group; The second multi-way valve group is fluidly connected to the second hydraulic cylinder group; The first oil inlet passage is fluidly connected to the output end of the large pump and fluidly connected to the first multi-way valve group; The second oil inlet passage is fluidly connected to the output end of the small pump and fluidly connected to the second multi-way valve group; The unloading circuit is fluidly connected to the oil tank, and the unloading circuit is fluidly connected to both the first multi-way valve group and the second multi-way valve group; An adjusting element is disposed between the second oil inlet passage and the first oil inlet passage, for disconnecting the second oil inlet passage from the first oil inlet passage and connecting the second oil inlet passage to the unloading circuit, so that the hydraulic control system is in a diversion state; and for unidirectionally connecting the second oil inlet passage to the first oil inlet passage, so that the hydraulic control system is in a confluence state.
[0006] In an optional embodiment, the adjusting element is a plug, a bridge joint, or a first check valve; When the hydraulic control system is in the diversion state, the plug, the bridge joint, or the first check valve is connected between the second oil inlet passage and the first oil inlet passage, and the second oil inlet passage is connected to the unloading circuit.
[0007] In an optional embodiment, the regulating element is a connecting pipe or a second one-way valve; When the hydraulic control system is in the confluence state, the connecting pipe or the second check valve is connected between the second oil inlet passage and the first oil inlet passage, and the second oil inlet passage is disconnected from the unloading circuit.
[0008] In an optional embodiment, the first cylinder group includes a pusher cylinder, a sliding plate cylinder, and a scraper cylinder, and the first multi-way valve group includes a first reversing valve fluidly connected to the pusher cylinder, a second reversing valve fluidly connected to the sliding plate cylinder, and a third reversing valve fluidly connected to the scraper cylinder. The first oil inlet passage is sequentially fluidly connected to the third reversing valve, the second reversing valve and the first reversing valve; The unloading circuit is fluidly connected to the first reversing valve, the second reversing valve, and the third reversing valve.
[0009] In an optional embodiment, the second cylinder group includes a feeding cylinder and a lifting cylinder, and the second multi-way valve group includes a fourth directional valve fluidly connected to the feeding cylinder and a fifth directional valve fluidly connected to the lifting cylinder. The second oil inlet passage is sequentially fluidly connected to the fifth directional valve and the fourth directional valve; The unloading circuit is fluidly connected to the fourth reversing valve and the fifth reversing valve.
[0010] In an optional embodiment, the second cylinder assembly further includes a locking hook cylinder, and a bidirectional electromagnetic ball valve is connected between the fifth directional valve and the rod chamber of the locking hook cylinder.
[0011] In an optional embodiment, the oil port A5 of the fifth directional valve is connected to the rod chamber of the lifting cylinder and the rod chamber of the locking hook cylinder, and the oil port B5 of the fifth directional valve is connected to the rodless chamber of the lifting cylinder and the rodless chamber of the locking hook cylinder.
[0012] In an optional embodiment, the rod chamber and rodless chamber of the lifting cylinder are connected by a one-way balance valve.
[0013] In an optional implementation, both the first multi-way valve assembly and the second multi-way valve assembly are integrally formed.
[0014] Secondly, this utility model provides a garbage compactor truck, including the garbage compactor truck hydraulic control system described in any of the foregoing embodiments.
[0015] The beneficial effects of the hydraulic control system for the garbage compactor truck and the garbage compactor truck provided in this embodiment of the invention include: An adjusting component is installed in the hydraulic control system. When the second oil inlet channel is disconnected from the first oil inlet channel, the first multi-way valve group is supplied with oil from the first oil inlet channel and returns oil from the unloading circuit, while the second multi-way valve group is supplied with oil from the second oil inlet channel and returns oil from the unloading circuit. At this time, the first cylinder group is in a diverted state. When the adjusting component connects the second oil inlet channel to the first oil inlet channel in one direction, the first cylinder group is supplied with oil not only through the large pump but also replenished with oil through the second oil inlet channel. At this time, the first cylinder group is in a confluence state. Thus, the hydraulic control system of this utility model can switch between the confluence state and the diverted state, which is applicable to the two mainstream types of garbage compactors, has the advantage of good versatility, and can effectively reduce the purchase cost of the hydraulic system. Attached Figure Description
[0016] To more clearly illustrate the technical solutions of the embodiments of this utility model, the drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this utility model 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.
[0017] Figure 1 This is a schematic diagram showing the hydraulic control system of the garbage compactor truck in a diversion state, as provided in this embodiment. Figure 2 This is a schematic diagram showing the hydraulic control system of the garbage compactor truck in a confluence state, as provided in this embodiment. Figure 3 A schematic diagram of the connection of the adjusting component in the diversion state of the hydraulic control system of the garbage compactor truck provided in this embodiment; Figure 4A schematic diagram of the connection of the adjusting component in the confluence state of the hydraulic control system of the garbage compactor truck provided in this embodiment; Figure 5 This is a partial hydraulic control schematic diagram of a Japanese-made compressor truck. Figure 6 This is a partial hydraulic control schematic diagram of an American-made compressor truck. Figure 7 This is a schematic diagram of the structure of the first multi-way valve group and the second multi-way valve group provided in this embodiment.
[0018] Icons: 10-Oil Tank; 100-First Cylinder Assembly; 110-Push Shovel Cylinder; 120-Slide Plate Cylinder; 130-Scraper Cylinder; 200-Second Cylinder Assembly; 210-Feeding Cylinder; 220-Lifting Cylinder; 230-Hook Locking Cylinder; 240-Two-Way Solenoid Ball Valve; 250-One-Way Balance Valve; 300-Double Pump; 310-Large Pump; 320-Small Pump; 400-First Multi-Way Valve Assembly; 410-First Directional Valve; 420-Second Directional Valve; 430-Third Directional Valve; 500-Second Multi-Way Valve Assembly; 510-Fourth Directional Valve; 520-Fifth Directional Valve; 610-First Oil Inlet Passage; 620-Second Oil Inlet Passage; 630-Unloading Circuit; 700 - Adjusting component; 810 - Filler lifting cylinder; 820 - Filler locking hook cylinder; 830 - Directional valve; 840 - Pipe-type hydraulic check valve; 850 - Solenoid ball valve; 860 - One-way throttle valve. Detailed Implementation
[0019] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. The components of the embodiments of this utility model described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.
[0020] Therefore, the following detailed description of the embodiments of the present 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 present invention without inventive effort are within the scope of protection of the present invention.
[0021] 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.
[0022] In the description of this utility model, 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 utility model product is usually placed during use, they are only for the convenience of describing this utility model 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 utility model.
[0023] Furthermore, the terms "first" and "second" are used only to distinguish descriptions and should not be interpreted as indicating or implying relative importance.
[0024] It should be noted that, where there is no conflict, the features in the embodiments of this utility model can be combined with each other.
[0025] Garbage compactor trucks are specialized urban sanitation vehicles that efficiently collect, compress, and transport garbage, making a significant contribution to improving urban environmental sanitation. Their main moving parts include scrapers, sliding plates, pushers, fillers, and lifting mechanisms, all driven by a hydraulic system.
[0026] Currently, the garbage compactor truck industry generally includes two types to meet different customer needs. The first type is the American-made compactor truck, which has a large capacity and high efficiency in compaction and filling cycles. The second type is the environmentally friendly and economical Japanese-made compactor truck. Due to the different characteristics of the two types of garbage compactor trucks, their hydraulic control principles and control logic cannot be unified: the drive system of the American-made compactor truck's actuation mechanism uses a combined large and small pump to supply oil to the pusher, scraper, and sliding plate, while the compactor is supplied with oil by a small pump. In contrast, the drive system of the Japanese-made compactor truck's actuation mechanism uses a large pump to supply oil to the pusher, scraper, and sliding plate, while the compactor is supplied with oil by a small pump. This is what the industry refers to as the Japanese-made compactor truck.
[0027] Due to the inconsistency in the drive systems of the motion mechanisms, the hydraulic system principles and control logic of the two types of garbage compactors are different. This results in poor versatility and limited applicability of the hydraulic systems, which is not conducive to the standardization of hydraulic systems and the reduction of purchase costs.
[0028] To address the problems of poor versatility, limited applicability, unsuitable standardization of hydraulic systems, and high purchase costs associated with current garbage compactor trucks, this utility model provides a hydraulic control system for a garbage compactor truck and the garbage compactor truck itself. The following detailed description, through embodiments and in conjunction with accompanying drawings, outlines the overall structure, working principle, and technical effects of the hydraulic control system and garbage compactor truck provided by this utility model.
[0029] On the one hand, this utility model provides a garbage compactor truck, belonging to sanitation vehicles, for the collection, compaction, and transfer of garbage. Specifically, the garbage compactor truck provided by this utility model includes a hydraulic control system.
[0030] Please refer to Figures 1-5 On the other hand, this utility model provides a hydraulic control system for a garbage compactor truck, which is applied to the aforementioned garbage compactor truck to control the movement of the moving parts, thereby performing actions such as pushing, loading, compressing, and lifting the garbage, and realizing the collection and compression of the garbage.
[0031] Please refer to Figure 1 and Figure 2 The hydraulic control system of the garbage compactor truck includes an oil tank 10, a first cylinder group 100, and a second cylinder group 200. The first cylinder group 100 drives the pusher, sliding plate, scraper, and other mechanisms to operate, while the second cylinder group 200 drives the loader to feed and lift materials. Furthermore, the hydraulic control system of the garbage compactor truck provided in this embodiment also includes a dual pump 300, a first multi-way valve group 400, a second multi-way valve group 500, a first oil inlet passage 610, a second oil inlet passage 620, an unloading circuit 630, and an adjusting component 700. The input end of the dual pump 300 is fluidly connected to the oil tank 10 and pumps hydraulic oil from the oil tank 10 to the first cylinder group 100 and the second cylinder group 200 to drive their operation. The dual pump 300 includes a large pump 310 and a small pump 320 connected in parallel. The first multi-way valve group 400 is fluidly connected to the first cylinder group 100 to control the flow direction and on / off state of the hydraulic oil entering the first cylinder group 100, thereby driving the first cylinder group 100 to perform different actions. The second multi-way valve group 500 is fluidly connected to the second cylinder group 200 to control the flow direction and on / off state of the hydraulic oil entering the second cylinder group 200, thereby driving the second cylinder group 200 to perform different actions. The first oil inlet passage 610 is fluidly connected to the output end P1 of the large pump 310, and the first oil inlet passage 610 is also fluidly connected to the first multi-way valve group 400, so that the large pump 310 supplies oil to the first multi-way valve group 400 through the first oil inlet passage 610. The second oil inlet passage 620 is fluidly connected to the output end P2 of the small pump 320, and the second oil inlet passage 620 is also fluidly connected to the second multi-way valve group 500, so that the small pump 320 supplies oil to the second multi-way valve group 500 through the second oil inlet passage 620. To return oil to the first cylinder group 100 and the second cylinder group 200 and form a complete oil circuit, the unloading circuit 630 is fluidly connected to the oil tank 10 and to the first multi-way valve group 400. The second oil inlet passage 620 is fluidly connected to the oil tank 10 and to the second multi-way valve group 500, so that oil can be returned to the first multi-way valve group 400 and the second multi-way valve group 500 through the unloading circuit 630. Furthermore, when the system merges, both the first multi-way valve group 400 and the second multi-way valve group 500 are unloaded through the first multi-way valve group 400; when the system splits, the second multi-way valve group 500 is directly connected to the unloading circuit 630 through the transition zone inside the multi-way valve for unloading.
[0032] Furthermore, the adjusting member 700 is disposed between the first oil inlet passage 610 and the second oil inlet passage 620. The adjusting member 700 enables the hydraulic control system in this embodiment to have a diversion state and a merging state. Specifically, when the hydraulic control system is in the diversion state, the adjusting member 700 disconnects the second oil inlet passage 620 from the first oil inlet passage 610; when the hydraulic control system is in the merging state, the adjusting member 700 enables the second oil inlet passage 620 to be unidirectionally connected to the first oil inlet passage 610.
[0033] In this invention, the first cylinder group 100 is controlled by the first multi-way valve group 400, and the second cylinder group 200 is controlled by the second multi-way valve group 500. An adjusting component 700 is provided in the hydraulic control system. When the second oil inlet channel 620 is disconnected from the first oil inlet channel 610, the first multi-way valve group 400 is supplied with oil from the first oil inlet channel 610 and returns oil from the unloading circuit 630. The second multi-way valve group 500 is supplied with oil from the second oil inlet channel 620 and returns oil from the unloading circuit 630 via the transition zone of the multi-way valve. This allows the large pump 310 to supply oil only to the first cylinder group 100, and the small pump 320 to supply oil only to the second cylinder group 200. The hydraulic control system is in a diversion state, resulting in a low flow rate requirement for the garbage compaction operation. When the adjusting component 700 allows the second oil inlet passage 620 to be unidirectionally connected to the first oil inlet passage 610, the first cylinder group 100 is not only supplied with oil by the large pump 310, but the second oil inlet passage 620 also replenishes oil to the first cylinder group 100, increasing the flow rate of the first cylinder group 100, thereby increasing the compaction volume and compaction speed. The adjusting component 700 allows the hydraulic control system of this invention to switch between confluence and diversion states, making it suitable for both mainstream types of garbage compactors. It has the advantage of good versatility and can effectively reduce the purchase cost of the hydraulic system.
[0034] The hydraulic control system can be adjusted between confluence and diversion states via the adjusting component 700. In the confluence state, the hydraulic control system exhibits the advantages of American compactor trucks (where the pusher, scraper, and slide block are supplied with oil by a combined large and small pump) – large capacity and high efficiency in compaction cycle operations. Conversely, in the diversion state, it offers the environmentally friendly and economical advantages of Japanese compactor trucks (where the pusher, scraper, and slide block are supplied with oil by a separate large pump). During operation, the hydraulic system can be adjusted to either confluence or diversion states according to actual working conditions, making it suitable for various situations, highly compatible, and widely applicable. Furthermore, the hydraulic control system provided in this embodiment unifies the control principles and logic of American and Japanese compactor trucks, using a multi-way valve of the same specification, resulting in a high degree of standardization.
[0035] Please refer to Figure 1 and Figure 3When the hydraulic control system is in a split-flow state, i.e., the second oil inlet channel 620 is disconnected from the first oil inlet channel 610, and the unloading circuit 630 is connected to the second oil inlet channel 620, both the first cylinder group 100 and the second cylinder group 200 return oil to the oil tank 10 through the unloading circuit 630. The second multi-way valve group 500 is connected to the unloading circuit 630 through the multi-way valve transition area oil passage for unloading. When the hydraulic control system is in a confluence state, i.e., the second oil inlet channel 620 is connected to the first oil inlet channel 610, the unloading circuit 630 is disconnected from the second oil inlet channel 620, and the second oil inlet channel 620 is used to replenish oil to the first oil inlet channel 610. At this time, both the first multi-way valve group 400 and the second multi-way valve group 500 are unloaded through the first multi-way valve group 400.
[0036] Please refer to Figure 2 and Figure 4 The adjusting component 700 is one of a plug, a bridge joint, or a first check valve. When the hydraulic control system is in the diversion state, the plug, bridge joint, or first check valve is connected between the second oil inlet passage 620 and the first oil inlet passage 610, and at this time the second oil inlet passage 620 is connected to the unloading circuit 630.
[0037] It is understood that, in the optional embodiments, please refer to Figure 3 a. When the adjusting element 700 is a plug, the second oil inlet passage 620 is disconnected from the first oil inlet passage 610 in the transition zone of the multi-way valve. At this time, the second oil inlet passage 620 is connected to the unloading circuit 630, and the hydraulic oil in the second oil inlet passage 620 returns directly to the oil tank 10 through the unloading circuit 630. The first cylinder group 100 is only supplied with oil by the large pump 310 alone, and the hydraulic control system is in a diversion state. In some optional embodiments, refer to Figure 3 b. The adjusting component 700 can also be a bridge joint. Since the bridge joint is in the open state, the second oil inlet passage 620 and the first oil inlet passage 610 are also in the open state in the transition zone of the multi-way valve. At this time, the second oil inlet passage 620 is connected to the unloading circuit 630, and the hydraulic oil in the second oil inlet passage 620 returns directly to the oil tank 10 through the unloading circuit 630. The first cylinder group 100 is only supplied with oil by the large pump 310 alone, and the hydraulic control system is in a diversion state. In some other optional embodiments, please refer to Figure 3c. When the regulating component 700 is the first check valve, a first check valve is installed between the second oil inlet passage 620 and the first oil inlet passage 610. Since the first check valve has a certain opening pressure, and the second oil inlet passage 620 is directly connected to the unloading circuit 630, the hydraulic oil will return to the oil tank through the second oil inlet passage 620 and the unloading circuit 630 without passing through the first check valve. At this time, the second oil inlet passage 620 and the first oil inlet passage 610 can also be regarded as being in a disconnected state. Thus, the second oil inlet passage 620 is connected to the unloading circuit 630, and the hydraulic oil in the second oil inlet passage 620 returns directly to the oil tank 10 through the unloading circuit 630. The first cylinder group 100 is only supplied with oil by the large pump 310 alone, and the hydraulic control system is in a diversion state.
[0038] When the hydraulic control system is in the confluence state, please refer to... Figure 2 and Figure 4 In an optional embodiment, please refer to Figure 4 d and Figure 4 e. The adjusting component 700 is a connecting pipe that directly connects the second oil inlet passage 620 to the first oil inlet passage 610. This allows the return oil from the second oil inlet passage 620 to enter the first oil inlet passage 610, thus supplying oil to the first cylinder group 100 through the combined flow of the first and second oil inlet passages 610 and 620. At this time, the second oil inlet passage 620 is disconnected from the unloading circuit 630. Specifically, in some optional embodiments, please refer to... Figure 4 d. A plug is provided between the second oil inlet passage 620 and the unloading circuit 630, so that the second oil inlet passage 620 and the unloading circuit 630 are disconnected in the transition zone of the multi-way valve. In some other optional embodiments, please refer to... Figure 4 e. A bridging joint is provided between the second oil inlet passage 620 and the unloading circuit 630, so that the second oil inlet passage 620 and the unloading circuit 630 are disconnected in the transition zone of the multi-way valve. In some other optional embodiments, please refer to Figure 4 f. The adjusting element 700 can also be a second check valve, which is connected between the second oil inlet passage 620 and the first oil inlet passage 610. The second check valve allows hydraulic oil to flow from the second oil inlet passage 620 towards the first oil inlet passage 610. At this time, the unloading circuit 630 is disconnected from the second oil inlet passage 620, and the hydraulic oil in the second oil inlet passage 620 will flow to the first oil inlet passage 610 through the second check valve. Thus, in the combined flow state, the large pump 310 and the small pump 320 achieve the effect of supplying oil to the first cylinder group 100 through combined flow.
[0039] Please refer to Figure 1 and Figure 2In this embodiment, the first cylinder group 100 includes a pusher cylinder 110, a sliding plate cylinder 120, and a scraper cylinder 130. The first multi-way valve group 400 includes a first directional valve 410 fluidly connected to the pusher cylinder 110, a second directional valve 420 fluidly connected to the sliding plate cylinder 120, and a third directional valve 430 fluidly connected to the scraper cylinder 130. Specifically, the rod-side and rodless sides of the pusher cylinder 110 are respectively connected to ports A1 and B1 of the first directional valve 410 via pipelines; the rod-side and rodless sides of the sliding plate cylinder 120 are respectively connected to ports A2 and B2 of the second directional valve 420 via pipelines; and the rod-side and rodless sides of the scraper cylinder 130 are respectively connected to ports A3 and B3 of the second directional valve 420 via pipelines. The first oil inlet passage 610 is fluidly connected to the third directional valve 430, the second directional valve 420, and the first directional valve 410 in sequence. The unloading circuit 630 is fluidly connected to the first directional valve 410, the second directional valve 420, and the third directional valve 430.
[0040] The first directional valve 410, the second directional valve 420, and the third directional valve 430 are all three-position six-way valves, with a neutral position, a first working position, and a second working position. When the first multi-way valve group 400 is in the neutral position, hydraulic oil returns directly from the first inlet oil passage 610 to the oil tank 10 through the unloading circuit 630, and the first multi-way valve group 400 is in the unloading state. When the first multi-way valve group 400 is in the first working position, hydraulic oil enters from the rodless chamber of the first cylinder group 100 through the first inlet oil passage 610 and returns from the rod chamber of the first cylinder group 100 through the unloading circuit 630 to drive the piston rods of the pusher cylinder 110, the slide plate cylinder 120, and the scraper cylinder 130 to extend. When the first multi-way valve group 400 is in the second working position, hydraulic oil enters from the rod chamber of the first cylinder group 100 through the first oil inlet passage 610 and returns from the rodless chamber of the first cylinder group 100 through the unloading circuit 630, thereby driving the piston rods of the pusher cylinder 110, the sliding plate cylinder 120, and the scraper cylinder 130 to retract. It can be understood that the first reversing valve 410, the second reversing valve 420, and the third reversing valve 430 can be switched simultaneously or separately, to control the pusher cylinder 110, the sliding plate cylinder 120, and the scraper cylinder 130 respectively.
[0041] Furthermore, in some optional embodiments, an overflow valve is connected between the first oil inlet passage 610 and the unloading circuit 630 to perform overflow pressure regulation when the pressure of the first multi-way valve group 400 is too high, thereby ensuring the system stability of the first multi-way valve group 400. Simultaneously, overflow valves are also connected between the scraper cylinder 130 and the unloading circuit 630, and between the pusher cylinder 110 and the unloading circuit 630, to perform overflow pressure regulation for the scraper cylinder 130 and the pusher cylinder 110, respectively.
[0042] Please refer to Figure 1and Figure 2 In this embodiment, the second cylinder group 200 includes a loading cylinder 210 and a lifting cylinder 220, and the second multi-way valve group 500 includes a fourth directional valve 510 fluidly connected to the loading cylinder 210 and a fifth directional valve 520 fluidly connected to the lifting cylinder 220. Specifically, the rod-side and rodless-side chambers of the loading cylinder 210 are respectively connected to ports A4 and B4 of the fourth directional valve 510 via pipelines; the rod-side chamber of the lifting cylinder 220 is connected to port A5 of the fifth directional valve 520, and the rodless-side chamber of the lifting cylinder 220 is connected to port B5 of the fifth directional valve 520. Further, the second oil inlet passage 620 is fluidly connected to the fifth directional valve 520 and the fourth directional valve 510 in sequence. The unloading circuit 630 is fluidly connected to the fourth directional valve 510 and the fifth directional valve 520.
[0043] Specifically, both the fourth directional valve 510 and the fifth directional valve 520 are three-position six-way valves, having a neutral position, a first working position, and a second working position. When either the fourth directional valve 510 or the fifth directional valve 520 is in the neutral position, hydraulic oil returns directly to the oil tank 10 through the second inlet oil passage 620 and the unloading circuit 630, and the fourth directional valve 510 or the fifth directional valve 520 is in the unloading state. When either the fourth directional valve 510 or the fifth directional valve 520 is in the first working position or the second working position, the piston rods of the loading cylinder 210 and the lifting cylinder 220 are in the extended or retracted state, respectively.
[0044] Furthermore, in some optional embodiments, an overflow valve is also connected between the second oil inlet passage 620 and the unloading circuit 630. The overflow valve is used to overflow and regulate the pressure of the second multi-way valve group 500 to prevent the pressure of the second oil inlet passage 620 from continuously increasing.
[0045] Please refer to Figure 1 and Figure 2 In some optional embodiments, the second cylinder group 200 further includes a locking hook cylinder 230. The rod chambers of both the lifting cylinder 220 and the locking hook cylinder 230 are connected to port A5 of the fifth directional valve 520. The rodless chambers of both the lifting cylinder 220 and the locking hook cylinder 230 are connected to port B5 of the fifth directional valve 520. A bidirectional solenoid ball valve 240 is also connected between the fifth directional valve 520 and the rod chamber of the locking hook cylinder 230. Furthermore, a one-way balance valve 250 is connected to both the rod chamber and the rodless chamber of the lifting cylinder 220.
[0046] When the filler needs to be lifted, the fifth directional valve 520 is switched so that the hydraulic oil input from the second oil inlet 620 flows out from the oil port B5. The two-way solenoid ball valve 240 is energized, and oil enters the rodless chamber of the locking hook cylinder 230 and returns oil to the rod chamber. Oil enters the rodless chamber of the lifting cylinder 220 and returns oil to the rod chamber. Due to the load pressure difference, the locking hook cylinder 230 first drives the locking hook to disengage. After the locking hook cylinder 230 has completed driving the locking hook to disengage, the lifting cylinder 220 extends to lift the filler. When the loader needs to descend, the fifth directional valve 520 first reverses, allowing hydraulic oil from the second oil inlet 620 to flow out through port A5 of the fifth directional valve 520. The hydraulic oil then enters the rod chamber of the lifting cylinder 220, causing the lifting cylinder 220 to retract and the loader to descend. During this process, the bidirectional solenoid ball valve 240 is not energized, and the locking hook remains in the disengaged state, allowing the loader to descend smoothly. Once the loader has descended to its designated position, the bidirectional solenoid ball valve 240 is energized, opening the oil circuit in the rod chamber of the locking hook cylinder 230. Oil then enters the rod chamber of the locking hook cylinder 230, driving the locking hook to lock. In this embodiment, a proximity switch is installed on the garbage bin. When the loader descends close to the proximity switch, the proximity switch senses this, controlling the bidirectional solenoid ball valve 240 to be energized. The specific control circuits and methods for the proximity switch and the bidirectional solenoid ball valve 240 are not limited here.
[0047] Please refer to Figure 5 , Figure 5 The hydraulic control diagram of a non-standard Japanese compactor truck shows that the actions of the filler lifting cylinder 810 and the filler locking hook cylinder 820 are controlled by a reversing valve 830. When the filler descends, the solenoid ball valve 850 needs to be energized to connect the oil circuit, allowing the filler to descend under its own weight. The descent speed is controlled by a one-way throttle valve 860. Therefore, the descent of the Japanese compactor truck's filler depends on the energization of the solenoid ball valve 850. If the solenoid ball valve 850 malfunctions, the filler will fail to descend. Since the filler lifting operation is typically used during unloading operations in landfills or incinerators, this makes disassembly and maintenance of the filler difficult, affecting the normal operation of the compactor truck. Furthermore, the loading device locking hook cylinder 820 is pressure maintained by a tubular hydraulic control check valve 840. When the tubular hydraulic control check valve 840 fails, or the cylinder leaks internally, or when the multi-way valves experience cross-contamination of oil between working connections, the locking hook will disengage. Troubleshooting this fault requires multiple checks, which affects work efficiency.
[0048] Please refer to Figure 6 , Figure 6This is a partial hydraulic control schematic diagram of a combined American-style compactor. In this American-style compactor, the loading unit lifting cylinder 810 and the loading unit locking hook cylinder 820 are each controlled by a separate directional valve 830. A tubular hydraulic control check valve 840 is connected to the rod chamber of the loading unit locking hook cylinder 820 to maintain pressure in the cylinder. If the tubular hydraulic control check valve 840 fails, or if there is internal leakage in the cylinder, or if there is cross-contamination between the working connections of the directional valves 830, the locking hook will disengage. Troubleshooting this fault requires multiple checks, which affects work efficiency.
[0049] Based on this, in this embodiment, a bidirectional electromagnetic ball valve 240 is connected between the fifth directional valve 520 and the locking hook cylinder 230. The bidirectional electromagnetic ball valve 240 is connected to the rod chamber of the locking hook cylinder 230. The bidirectional electromagnetic ball valve 240 is normally in a bidirectional cut-off position. By setting the bidirectional electromagnetic ball valve 240, the situation where pressure oil opens the tubular hydraulic control check valve 840 due to internal leakage of the directional valve 830 core, causing disengagement, can be effectively avoided in traditional compactor trucks. Furthermore, a pressure testing hole is provided on the valve body of the bidirectional electromagnetic ball valve 240 for communication with the rod chamber of the locking hook cylinder 230. When abnormal disengagement occurs, the pressure in the rod chamber of the locking hook cylinder 230 can be measured immediately through the pressure testing hole to determine whether there is internal leakage in the cylinder, reducing the risk of failure and improving the efficiency of fault diagnosis. Furthermore, by setting a one-way balance valve 250, the problem that the descent of the compactor in traditional garbage compactor trucks depends on the energization of the solenoid valve is improved. When the traditional solenoid valve fails, the compactor will not be able to descend. When the solenoid valve malfunctions, the one-way balance valve 250 can adjust the opening pressure to allow the compactor to descend slowly, improving the safety of the garbage compactor. Furthermore, by connecting the one-way balance valve 250 to the oil inlet and outlet of the lifting cylinder 220, pressure is maintained in the lifting cylinder 220, preventing a sudden drop of the compactor and potential safety accidents caused by pressure loss due to oil circuit malfunctions.
[0050] Therefore, in this embodiment, a two-way electromagnetic ball valve 240 and a one-way balance valve 250 are set, and the lifting cylinder 220 and the locking hook cylinder 230 are controlled by the same multi-way valve (fifth directional valve 520). Compared with traditional Japanese compression trucks, combined with Figure 5 The hydraulic control system provided in this embodiment improves the filler lifting cylinder 810 into a double-acting lifting cylinder 220 with a one-way balance valve 250. This improves upon the shortcomings of Japanese compactor trucks, where the electromagnetic ball valve 850 controls the oil circuit, the filler relies on its own weight to fall, and it cannot fall without power. The locking reliability of the filler locking hook cylinder 820 is ensured by the bidirectional electromagnetic ball valve 240. Compared to traditional American compactor trucks, this system combines… Figure 6In this embodiment, the lifting cylinder 220 and the locking hook cylinder 230 in the hydraulic control system are controlled by the same multi-way valve, reducing the number of multi-way valves and eliminating the tubular hydraulic control check valve 840 with rod chamber in the filler locking hook cylinder 820, thus reducing the risk of failure and improving the efficiency of fault diagnosis.
[0051] Please refer to Figure 7 In this embodiment, the first multi-way valve group 400 and the second multi-way valve group 500 are both integrally formed, that is, the first reversing valve 410, the second reversing valve 420, the third reversing valve 430, the fourth reversing valve 510, and the fifth reversing valve 520 are all integrally formed. This improves upon the problem of traditional multi-way valves being assembled from multiple valve plates, resulting in low structural strength and easy leakage between multiple valve plates.
[0052] In summary, the hydraulic control system for the garbage compactor truck and the implementation principle of the garbage compactor truck provided by this utility model are as follows: by adding an adjusting component 700 to the hydraulic control system, the hydraulic control system of this utility model can switch between the merging state and the splitting state, making American and Japanese garbage compactor trucks interchangeable and unifying the control principles of the two types of garbage compactor trucks. It is applicable to the two mainstream types of garbage compactor trucks, has the advantage of good versatility, and can effectively reduce the purchase cost of the hydraulic system.
[0053] The above description is only a specific embodiment of this utility model, but the protection scope of this utility model is not limited thereto. Any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this utility model should be included within the protection scope of this utility model.
Claims
1. A hydraulic control system for a garbage compactor truck, comprising an oil tank (10), a first cylinder group (100), and a second cylinder group (200), characterized in that, The hydraulic control system also includes: A tandem pump (300) is provided, the input end of which is fluidly connected to the oil tank, and the tandem pump includes a large pump (310) and a small pump (320). The first multi-way valve group (400) is fluidly connected to the first hydraulic cylinder group (100); The second multi-way valve assembly (500) is fluidly connected to the second hydraulic cylinder assembly (200); The first oil inlet passage (610) is fluidly connected to the output end P1 of the large pump (310) and fluidly connected to the first multi-way valve group (400); The second oil inlet passage (620) is fluidly connected to the output end P2 of the small pump (320) and fluidly connected to the second multi-way valve group (500); The unloading circuit (630) is fluidly connected to the oil tank (10), and the unloading circuit (630) is fluidly connected to both the first multi-way valve group (400) and the second multi-way valve group (500). An adjusting member (700) is disposed between the second oil inlet passage (620) and the first oil inlet passage (610) for disconnecting the second oil inlet passage (620) from the first oil inlet passage (610) and connecting the second oil inlet passage (620) to the unloading circuit (630) so that the hydraulic control system is in a diversion state; and for unidirectionally connecting the second oil inlet passage (620) to the first oil inlet passage (610) so that the hydraulic control system is in a confluence state.
2. The hydraulic control system for the garbage compactor truck according to claim 1, characterized in that, The adjusting component (700) is a plug, a bridge joint, or a first check valve; When the hydraulic control system is in the diversion state, the plug, the bridge joint or the first check valve is connected between the second oil inlet passage (620) and the first oil inlet passage (610), and the second oil inlet passage (620) is connected to the unloading circuit (630).
3. The hydraulic control system for the garbage compactor truck according to claim 1, characterized in that, The regulating component (700) is a connecting pipe or a second one-way valve; When the hydraulic control system is in the confluence state, the connecting pipe or the second check valve is connected between the second oil inlet passage (620) and the first oil inlet passage (610), and the second oil inlet passage (620) is disconnected from the unloading circuit (630).
4. The hydraulic control system for the garbage compactor truck according to claim 1, characterized in that, The first cylinder group (100) includes a pusher cylinder (110), a sliding plate cylinder (120) and a scraper cylinder (130). The first multi-way valve group (400) includes a first reversing valve (410) fluidly connected to the pusher cylinder (110), a second reversing valve (420) fluidly connected to the sliding plate cylinder (120), and a third reversing valve (430) fluidly connected to the scraper cylinder (130). The first oil inlet passage (610) is sequentially fluidly connected to the third reversing valve (430), the second reversing valve (420) and the first reversing valve (410); The unloading circuit (630) is fluidly connected to the first reversing valve (410), the second reversing valve (420), and the third reversing valve (430).
5. The hydraulic control system for the garbage compactor truck according to claim 1, characterized in that, The second cylinder group (200) includes a feeding cylinder (210) and a lifting cylinder (220), and the second multi-way valve group (500) includes a fourth directional valve (510) fluidly connected to the feeding cylinder (210) and a fifth directional valve (520) fluidly connected to the lifting cylinder (220). The second oil inlet passage (620) is sequentially fluidly connected to the fifth directional valve (520) and the fourth directional valve (510); The unloading circuit (630) is fluidly connected to the fourth reversing valve (510) and the fifth reversing valve (520).
6. The hydraulic control system for the garbage compactor truck according to claim 5, characterized in that, The second cylinder group (200) also includes a locking hook cylinder (230), and a two-way electromagnetic ball valve (240) is connected between the fifth directional valve (520) and the rod chamber of the locking hook cylinder (230).
7. The hydraulic control system for the garbage compactor truck according to claim 6, characterized in that, The oil port A5 of the fifth directional valve (520) is connected to the rod chamber of the lifting cylinder (220) and the rod chamber of the locking hook cylinder (230), and the oil port B5 of the fifth directional valve (520) is connected to the rodless chamber of the lifting cylinder (220) and the rodless chamber of the locking hook cylinder (230).
8. The hydraulic control system for the garbage compactor truck according to claim 6, characterized in that, The rod chamber and rodless chamber of the lifting cylinder (220) are both connected to a one-way balance valve (250).
9. The hydraulic control system for the garbage compactor truck according to claim 1, characterized in that, Both the first multi-way valve group (400) and the second multi-way valve group (500) are integrally formed.
10. A garbage compactor truck, characterized in that, The hydraulic control system for the garbage compactor truck as described in any one of claims 1-9.