Hydraulic control system of garbage compression truck and garbage compression truck

Abstract

The embodiment of the invention provides a hydraulic control system of a garbage compression truck and the garbage compression truck, and relates to the field of garbage compression trucks. The hydraulic control system of the garbage compression truck comprises an oil cylinder, a first oil cylinder set, a second oil cylinder set, a double pump, a first multi-way valve set, a second multi-way valve set, a first oil inlet channel, a second oil inlet channel, an unloading loop and an adjusting piece, and the adjusting piece is arranged between the second oil inlet channel and the first oil inlet channel. The first oil inlet channel is used for disconnecting the second oil inlet channel from the first oil inlet channel and communicating the second oil inlet channel with the unloading loop, so that the hydraulic control system is in a shunting state; the second oil inlet channel is in one-way communication with the first oil inlet channel, and the hydraulic control system is in a confluence state. The garbage compression truck provided by the invention comprises the garbage compression truck hydraulic control system. The hydraulic system can be suitable for two kinds of mainstream garbage compression trucks and is good in universality, and the acquisition cost of the hydraulic system can be effectively reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of garbage compression vehicles, and in particular to a hydraulic control system of a garbage compression vehicle and a garbage compression vehicle. Background Art

[0002] Garbage compactors are specialized urban sanitation vehicles that efficiently collect and transport garbage, making a significant contribution to improving urban environmental sanitation. Their main components, including scrapers, slides, pushers, fillers, and lift mechanisms, are all driven by a hydraulic system.

[0003] Currently, garbage compactors in the industry generally fall into two categories, tailored to different customer needs: American-made compactors with large capacity and efficient compression and filling cycles, and Japanese-made compactors with environmentally friendly and economical designs. Due to the distinct characteristics of these two types of compactors, their hydraulic system principles and control logic differ, resulting in limited versatility and a limited range of applications. This hinders the standardization of hydraulic systems and reduces acquisition costs. Summary of the Invention

[0004] The purpose of the present invention includes providing a garbage compression truck hydraulic control system and a garbage compression truck, which can be applicable to two mainstream types of garbage compression trucks, has the advantages of good versatility, and can effectively reduce the purchase cost of the hydraulic system.

[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, comprising a fuel tank, a first cylinder group, and a second cylinder group, the hydraulic control system further comprising: a double pump, wherein an input end of the double pump is fluidically connected to the oil tank, and the double pump comprises a large pump and a small pump; a first multi-way valve group, fluidically connected to the first cylinder group; a second multi-way valve group, fluidically connected to the second cylinder group; a first oil inlet passage, fluidically connected to the output end of the large pump and fluidically connected to the first multi-way valve group; a second oil inlet passage, fluidically connected to the output end of the small pump and fluidically connected to the second multi-way valve group; an unloading circuit, fluidically 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 member is provided between the second oil inlet passage and the first oil inlet passage, and is used to disconnect the second oil inlet passage from the first oil inlet passage and connect the second oil inlet passage with the unloading circuit so that the hydraulic control system is in a diversion state; and is used to connect the second oil inlet passage unidirectionally toward the first oil inlet passage so that the hydraulic control system is in a merging state.

[0006] In an optional embodiment, the regulating member is a plug, a bridge joint or a first one-way valve; When the hydraulic control system is in the diversion state, the plug, the bridge joint or the first one-way valve is connected between the second oil inlet passage and the first oil inlet passage, and the second oil inlet passage is communicated with the unloading circuit.

[0007] In an optional embodiment, the regulating member is a connecting pipe or a second one-way valve; When the hydraulic control system is in the merging state, the connecting pipe or the second one-way 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 dozer blade cylinder, a slide plate cylinder, and a scraper cylinder, and the first multi-way valve group includes a first reversing valve fluidically connected to the dozer blade cylinder, a second reversing valve fluidly connected to the slide plate cylinder, and a third reversing valve fluidly connected to the scraper cylinder; The first oil inlet passage is fluidically connected to the third reversing valve, the second reversing valve and the first reversing valve in sequence; The unloading circuit is fluidically 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 reversing valve fluidically connected to the feeding cylinder and a fifth reversing valve fluidly connected to the lifting cylinder; The second oil inlet passage is fluidically connected to the fifth reversing valve and the fourth reversing valve in sequence; The unloading circuit is fluidically 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 two-way electromagnetic ball valve is connected between the fifth reversing valve and the rod chamber of the locking hook cylinder.

[0011] In an optional embodiment, the oil port A5 of the fifth reversing 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 reversing 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 the rodless chamber of the lifting cylinder are connected to a one-way balancing valve.

[0013] In an optional embodiment, the first multi-way valve group and the second multi-way valve group are both integrally formed.

[0014] In a second aspect, the present invention provides a garbage compression truck comprising the hydraulic control system for the garbage compression truck as described in any one of the aforementioned embodiments.

[0015] The hydraulic control system and the garbage compression truck provided by the embodiments of the present invention have the following beneficial effects: The camming control system is constructed so that when the camming control system is in operation, the camming engine can be turned away from the loadsheet and the loadsheet can be turned away from the loadsheet. The camming control system can be turned away from the loadsheet and the loadsheet can be turned away from the loadsheet. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments. It should be understood that the following drawings only illustrate certain embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other relevant drawings can be obtained based on these drawings without paying any creative work.

[0017] Figure 1 A schematic diagram of the hydraulic control system of the garbage compactor provided in this embodiment in a diversion state; Figure 2 A schematic diagram of the hydraulic control system of the garbage compression truck provided in this embodiment in a merging state; Figure 3 A schematic diagram of the connection of the regulating components of the hydraulic control system of the garbage compacting truck provided in this embodiment in the diversion state; Figure 4A schematic diagram of the connection of the regulating components of the hydraulic control system of the garbage compacting truck provided in this embodiment in the merging state; Figure 5 This is a partial hydraulic control schematic diagram of a Japanese compression truck; Figure 6 This is a partial hydraulic control schematic diagram of an American compression truck; Figure 7 This is a schematic structural diagram of the first multi-way valve group and the second multi-way valve group provided in this embodiment.

[0018] Icons: 10-Fuel tank; 100-First cylinder group; 110-Busting cylinder; 120-Skateboard cylinder; 130-Scraper cylinder; 200-Second cylinder group; 210-Loading cylinder; 220-Lifting cylinder; 230-Hook cylinder; 240-Two-way solenoid ball valve; 250-One-way balancing valve; 300-Double pump; 310-Large pump; 320-Small pump; 400-First multi-way valve group; 410-First reversing valve; 420-Second reversing valve; 430-Third reversing valve; 500-Second multi-way valve group; 510-Fourth reversing valve; 520-Fifth reversing valve; 610-First oil inlet channel; 620-Second oil inlet channel; 630-Unloading circuit; 700-adjusting part; 810-loader lifting cylinder; 820-loader locking hook cylinder; 830-reversing valve; 840-tubular hydraulically controlled one-way valve; 850-electromagnetic ball valve; 860-one-way throttle valve. DETAILED DESCRIPTION

[0019] To make the objectives, technical solutions, and advantages of the embodiments of the present invention more clear, the technical solutions of the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings herein can 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 invention as claimed, but rather merely represents selected embodiments of the present invention. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without creative effort are intended to fall within the scope of protection of the present invention.

[0021] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further defined or explained in subsequent drawings.

[0022] In the description of the present invention, it should be noted that if the terms "upper", "lower", "inside", "outside", etc. appear, the orientation or position relationship indicated is based on the orientation or position relationship shown in the accompanying drawings, or is the orientation or position relationship in which the product of the invention is usually placed when in use. It is only for the convenience of describing the present invention and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be understood as a limitation on the present invention.

[0023] In addition, the terms "first", "second", etc., if used, are merely used to distinguish and describe, and should not be understood as indicating or implying relative importance.

[0024] It should be noted that, in the absence of conflict, the features in the embodiments of the present invention may be combined with each other.

[0025] Garbage compactors are specialized urban sanitation vehicles that efficiently collect, compress, and transport garbage, making a significant contribution to improving urban sanitation. Their main components, including scrapers, slides, pushers, fillers, and lift mechanisms, are all driven by a hydraulic system.

[0026] Currently, garbage compactors in the industry generally fall into two categories, tailored to different customer needs. The first is the American-made compactor, characterized by its large capacity and efficient compression and filling cycle, while the other is the environmentally friendly and economical Japanese-made compactor. Due to their distinct characteristics, their hydraulic control principles and logic differ: The driving mechanism of American compactors utilizes a combined oil supply for the pusher, scraper, and slide plate from large and small pumps, while the filler is supplied with a separate oil supply from a small pump. Japanese compactors, on the other hand, utilize a separate oil supply for the pusher, scraper, and slide plate from a large pump, while the filler is supplied with a separate oil supply from a small pump. These compactors are referred to in the industry as "Japanese compactors."

[0027] Due to the inconsistency of the action mechanism drive system, the hydraulic system principles and control logic of the two types of garbage compactors are different. The hydraulic system has poor versatility and a small scope of application, which is not conducive to the standardization of the hydraulic system and the reduction of purchase costs.

[0028] To address the current problems of garbage compression trucks, such as poor versatility, limited applicability, limited standardization of hydraulic systems, and high purchase costs, the present invention provides a hydraulic control system for a garbage compression truck and a garbage compression truck. The following describes in detail the overall structure, operating principle, and technical effects of the hydraulic control system and garbage compression truck provided by the present invention, using examples and accompanying drawings.

[0029] In one aspect, the present invention provides a garbage compression truck, which is a sanitation vehicle and is used for collecting, compressing and transporting garbage. The garbage compression truck provided by the present invention includes a hydraulic control system for the garbage compression truck.

[0030] Please refer to Figure 1-Figure 5 On the other hand, the present invention provides a hydraulic control system for a garbage compression truck, which is applied to the above-mentioned garbage compression truck to control the movement of the action parts, thereby pushing, loading, compressing, lifting and other actions on the garbage to achieve the collection and compression of the garbage.

[0031] Please refer to Figure 1 and Figure 2 The hydraulic control system of the garbage compacting vehicle includes a fuel tank 10, a first cylinder group 100, and a second cylinder group 200. The first cylinder group 100 is used to drive the push shovel, slide plate, scraper and other mechanisms to operate, and the second cylinder group 200 is used to drive the filler to load and lift. Furthermore, the hydraulic control system of the garbage compacting vehicle provided by the embodiment of the present invention also includes a double pump 300, a first multi-way valve group 400, a second multi-way valve group 500, a first oil inlet channel 610, a second oil inlet channel 620, an unloading circuit 630, and an adjusting member 700. The input end of the double pump 300 is fluidically connected to the fuel tank 10, and is used to pump the hydraulic oil in the fuel tank 10 to the first cylinder group 100 and the second cylinder group 200 to drive the first cylinder group 100 and the second cylinder group 200 to operate. The double pump 300 includes a large pump 310 and a small pump 320 connected in parallel. The first multi-way valve block 400 is fluidically connected to the first cylinder group 100 to control the flow direction and on / off of hydraulic oil entering the first cylinder group 100, thereby driving the first cylinder group 100 to perform various operations. The second multi-way valve block 500 is fluidically connected to the second cylinder group 200 to control the flow direction and on / off of hydraulic oil entering the second cylinder group 200, thereby driving the second cylinder group 200 to perform various operations. The first oil inlet passage 610 is fluidically connected to the output terminal P1 of the large pump 310. The first oil inlet passage 610 is fluidically connected to the first multi-way valve block 400, so that the large pump 310 supplies oil to the first multi-way valve block 400 through the first oil inlet passage 610. The second oil inlet passage 620 is fluidically connected to the output terminal P2 of the small pump 320. The second oil inlet passage 620 is fluidically connected to the second multi-way valve block 500, so that the small pump 320 supplies oil to the second multi-way valve block 500 through the second oil inlet passage 620. To return oil to the first and second cylinder groups 100 and 200, thereby forming a complete oil circuit, the unloading circuit 630 is fluidly connected to the oil tank 10 and the first multi-way valve group 400. The second oil inlet passage 620 is fluidly connected to the oil tank 10 and the second multi-way valve group 500, thereby returning oil to the first and second multi-way valve groups 400 and 500 through the unloading circuit 630. Furthermore, when the systems merge, both the first and second multi-way valve groups 400 and 500 are unloaded through the first multi-way valve group 400. When the systems diverge, the second multi-way valve group 500 is directly connected to the unloading circuit 630 through the transition zone inside the multi-way valve group for unloading.

[0032] Furthermore, a regulating member 700 is disposed between the first oil inlet passage 610 and the second oil inlet passage 620. The regulating member 700 enables the hydraulic control system of this embodiment to have a diverging state and a merging state. When the hydraulic control system is in the diverging state, the regulating 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 regulating member 700 allows the second oil inlet passage 620 to unidirectionally connect to the first oil inlet passage 610.

[0033] In the present invention, the movement of the first cylinder group 100 is controlled by the first multi-way valve group 400, and the movement of the second cylinder group 200 is controlled by the second multi-way valve group 500; and an adjusting member 700 is provided in the hydraulic control system. The adjusting member 700 enables the first multi-way valve group 400 to be supplied with oil by the first oil inlet channel 610 and return oil from the unloading circuit 630 when the second oil inlet channel 620 is disconnected from the first oil inlet channel 610, and the second multi-way valve group 500 to be supplied with oil by the second oil inlet channel 620 and return oil from the unloading circuit 630 through the second oil inlet channel 620 in the transition area of ​​the multi-way valve, so that the large pump 310 supplies oil to the first cylinder group 100 alone, and the small pump 320 supplies oil to the second cylinder group 200 alone, the hydraulic control system is in a diversion state, and the flow demand of the garbage filling operation is small. When the adjustment member 700 connects the second oil inlet passage 620 to the first oil inlet passage 610 in a one-way manner, 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 and, in turn, the filling volume and speed. The provision of the adjustment member 700 enables the hydraulic control system of the present invention to switch between merging and diverging states, making it suitable for both mainstream garbage compacting trucks, offering the advantages of high versatility and effectively reducing the acquisition cost of the hydraulic system.

[0034] Adjustment member 700 adjusts the hydraulic control system between merging and diverging states. This allows the hydraulic control system to, in the merging state, exhibit the large capacity and efficient compression and filling cycle characteristics of American compacting trucks (where the pusher blade, scraper, and slide plate are supplied by a combined large and small pump); or, in the diverging state, exhibit the environmental and economic advantages of Japanese compacting trucks (where the pusher blade, scraper, and slide plate are supplied by separate large pumps). Adjusting the hydraulic system to either merging or diverging states during operation, depending on actual operating conditions, allows for wide compatibility and adaptability. Furthermore, the hydraulic control system provided in this embodiment integrates the control principles and logic of American and Japanese compacting trucks, utilizing a multi-way valve of the same specifications for control, resulting in a high degree of commonality.

[0035] Please refer to Figure 1 and Figure 3When the hydraulic control system is in a diverting state, that is, the second oil inlet passage 620 is disconnected from the first oil inlet passage 610, the unloading circuit 630 is connected to the second oil inlet passage 620, and the first cylinder group 100 and the second cylinder group 200 both 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 zone oil passage for unloading. When the hydraulic control system is in a merging state, that is, the second oil inlet passage 620 and the first oil inlet passage 610 are connected, the unloading circuit 630 is disconnected from the second oil inlet passage 620, and the second oil inlet passage 620 is used to replenish oil to the first oil inlet passage 610. At this time, the first multi-way valve group 400 and the second multi-way valve group 500 both unload through the first multi-way valve group 400.

[0036] Please refer to Figure 2 and Figure 4 The regulating member 700 is one of a plug, a bridge joint or a first one-way valve. When the hydraulic control system is in the diversion state, the plug, the bridge joint or the first one-way valve is connected between the second oil inlet channel 620 and the first oil inlet channel 610, and at this time the second oil inlet channel 620 is connected to the unloading circuit 630.

[0037] It is understood that in an optional embodiment, please refer to Figure 3 a. When the regulating member 700 is in the plugging position, 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. The hydraulic oil in the second oil inlet passage 620 is directly returned to the oil tank 10 through the unloading circuit 630. The first cylinder group 100 is supplied with oil only through the large pump 310. The hydraulic control system is in a diversion state. In some optional embodiments, refer to Figure 3 b. The regulating member 700 can also be a bridge joint. Since the bridge joint is in the disconnected state, the second oil inlet channel 620 and the first oil inlet channel 610 are also in the disconnected state in the transition zone of the multi-way valve. At this time, the second oil inlet channel 620 is connected to the unloading circuit 630. The hydraulic oil in the second oil inlet channel 620 is directly returned to the oil tank 10 through the unloading circuit 630. The first cylinder group 100 is only supplied with oil through the large pump 310. The hydraulic control system is in a diversion state. In other optional embodiments, please refer to Figure 3c. When the regulating member 700 is a first one-way valve, the first one-way valve is installed between the second oil inlet passage 620 and the first oil inlet passage 610. Since the first one-way valve has a certain opening pressure, the second oil inlet passage 620 and the unloading circuit 630 are directly connected. Therefore, the hydraulic oil will return to the fuel tank through the second oil inlet passage 620 and the unloading circuit 630 without passing through the first one-way valve. At this time, the second oil inlet passage 620 and the first oil inlet passage 610 can be considered to be in a disconnected state. As a result, the second oil inlet passage 620 and the unloading circuit 630 are connected, and the hydraulic oil in the second oil inlet passage 620 is directly returned to the fuel tank 10 through the unloading circuit 630. The first cylinder group 100 is supplied with oil solely by the large pump 310, and the hydraulic control system is in a diverted state.

[0038] When the hydraulic control system is in the merge state, please refer to Figure 2 and Figure 4 In an optional embodiment, please refer to Figure 4 d and Figure 4 e. The regulating member 700 is a connecting pipe that directly connects the second oil inlet passage 620 with the first oil inlet passage 610, so that the return oil of the second oil inlet passage 620 enters the first oil inlet passage 610, and the first oil cylinder group 100 is supplied with oil through the first oil inlet passage 610 and the second oil inlet passage 620. At this time, the second oil inlet passage 620 is disconnected from the unloading circuit 630. Specifically, in some selected 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 other optional embodiments, please refer to Figure 4 e. A bridge 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 area of ​​the multi-way valve. In other optional embodiments, please refer to Figure 4 f. The regulating member 700 can also be a second one-way valve connected between the second oil inlet passage 620 and the first oil inlet passage 610. The second one-way valve allows hydraulic oil to flow from the second oil inlet passage 620 to 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 through the second one-way valve to the first oil inlet passage 610. Thus, in the merging state, the large pump 310 and the small pump 320 merge to supply oil to the first cylinder group 100.

[0039] Please refer to Figure 1 and Figure 2In this embodiment, the first cylinder group 100 includes a dozer cylinder 110, a slide cylinder 120, and a scraper cylinder 130. The first multi-way valve group 400 includes a first reversing valve 410 fluidically connected to the dozer cylinder 110, a second reversing valve 420 fluidically connected to the slide cylinder 120, and a third reversing valve 430 fluidically connected to the scraper cylinder 130. Specifically, the rod chamber and rodless chamber of the dozer cylinder 110 are connected to ports A1 and B1 of the first reversing valve 410 via pipelines, respectively; the rod chamber and rodless chamber of the slide cylinder 120 are connected to ports A2 and B2 of the second reversing valve 420 via pipelines, respectively; and the rod chamber and rodless chamber of the scraper cylinder 130 are connected to ports A3 and B3 of the second reversing valve 420 via pipelines, respectively. The first oil inlet passage 610 is fluidically connected to the third reversing valve 430, the second reversing valve 420, and the first reversing valve 410 in sequence. The unloading circuit 630 is fluidically connected to the first reversing valve 410, the second reversing valve 420, and the third reversing valve 430.

[0040] The first reversing valve 410, the second reversing valve 420, and the third reversing valve 430 are all three-position, six-way valves having a neutral position, a first operating position, and a second operating position. When the first multi-way valve assembly 400 is in the neutral position, hydraulic oil is directly returned from the first oil inlet passage 610 to the oil tank 10 via the unloading circuit 630, and the first multi-way valve assembly 400 is in an unloaded state. When the first multi-way valve assembly 400 is in the first operating position, hydraulic oil enters the rodless chamber of the first cylinder assembly 100 through the first oil inlet passage 610 and returns from the rod chamber of the first cylinder assembly 100 via the unloading circuit 630, thereby driving the piston rods of the dozer cylinder 110, the slide cylinder 120, and the scraper cylinder 130 to extend. When the first multi-way valve assembly 400 is in the second operating position, hydraulic oil enters the rod chamber of the first cylinder assembly 100 through the first oil inlet passage 610 and returns from the rodless chamber of the first cylinder assembly 100 through the unloading circuit 630, thereby retracting the piston rods of the dozer cylinder 110, the slide cylinder 120, and the scraper cylinder 130. It will be appreciated that the first, second, and third reversing valves 410, 420, and 430 can be switched simultaneously or separately to control the dozer cylinder 110, the slide cylinder 120, and the scraper cylinder 130, respectively.

[0041] Furthermore, in some optional embodiments, a relief valve is connected between the first oil inlet passage 610 and the unloading circuit 630 to provide relief and pressure regulation when the pressure in the first multi-way valve assembly 400 is too high, thereby ensuring system stability of the first multi-way valve assembly 400. Simultaneously, relief 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 provide relief and pressure regulation for the scraper cylinder 130 and the pusher cylinder 110.

[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 assembly 500 includes a fourth reversing valve 510 fluidically connected to the loading cylinder 210 and a fifth reversing valve 520 fluidically connected to the lifting cylinder 220. Specifically, the rod chamber and rodless chamber of the loading cylinder 210 are connected to ports A4 and B4 of the fourth reversing valve 510 via pipelines, respectively; the rod chamber of the lifting cylinder 220 is connected to port A5 of the fifth reversing valve 520, and the rodless chamber of the lifting cylinder 220 is connected to port B5 of the fifth reversing valve 520. Furthermore, the second oil inlet passage 620 is fluidically connected to the fifth reversing valve 520 and the fourth reversing valve 510, respectively. The unloading circuit 630 is fluidically connected to the fourth reversing valve 510 and the fifth reversing valve 520.

[0043] Specifically, the fourth reversing valve 510 and the fifth reversing valve 520 are both three-position, six-way valves, each having a neutral position, a first working position, and a second working position. When the fourth reversing valve 510 or the fifth reversing valve 520 is in the neutral position, hydraulic oil returns directly to the oil tank 10 via the second oil inlet passage 620 and the unloading circuit 630, and the fourth reversing valve 510 or the fifth reversing valve 520 is in an unloading state. When the fourth reversing valve 510 or the fifth reversing 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 respectively extended or retracted.

[0044] Furthermore, in some optional embodiments, a relief valve is also connected between the second oil inlet channel 620 and the unloading circuit 630, and the relief valve is used to perform overflow pressure regulation on the second multi-way valve group 500 to prevent the pressure of the second oil inlet channel 620 from continuing to rise.

[0045] Please refer to Figure 1 and Figure 2 In some optional embodiments, the second cylinder group 200 further includes a hook cylinder 230. The rod chambers of the lifting cylinder 220 and the hook cylinder 230 are both connected to port A5 of the fifth reversing valve 520. The rodless chambers of the lifting cylinder 220 and the hook cylinder 230 are both connected to port B5 of the fifth reversing valve 520. A two-way electromagnetic ball valve 240 is also connected between the fifth reversing valve 520 and the rod chamber of the hook cylinder 230. Furthermore, a one-way balancing valve 250 is connected to both the rod chamber and the rodless chamber of the lifting cylinder 220.

[0046] When it is necessary to drive the loader to lift, the fifth reversing valve 520 is reversed so that the hydraulic oil input from the second oil inlet channel 620 flows out from the oil port B5, the two-way electromagnetic ball valve 240 is energized, the rodless chamber of the locking hook cylinder 230 is supplied with oil, and the rod chamber is returned with oil, the rodless chamber of the lifting cylinder 220 is supplied with oil, and the rod chamber is returned with oil. Due to the load pressure difference, the locking hook cylinder 230 first drives the locking hook to unhook. After the locking hook cylinder 230 has driven the locking hook to unhook, the lifting cylinder 220 extends to lift the loader. When the loader needs to be lowered, the fifth reversing valve 520 first switches direction, allowing hydraulic oil from the second oil inlet passage 620 to flow out of port A5 of the fifth reversing valve 520. The hydraulic oil then enters the rod chamber of the lift cylinder 220, causing it to retract and the loader to descend. During this process, the two-way solenoid valve 240 is de-energized, keeping the hook unhooked, allowing the loader to descend smoothly. When the loader is lowered into position, the two-way solenoid valve 240 is energized, opening the oil passage in the rod chamber of the hook cylinder 230. Oil enters the rod chamber of the hook cylinder 230, driving the hook to lock. In this embodiment, a proximity switch is installed on the waste bin. When the loader descends close to the proximity switch, the proximity switch generates a signal, controlling the power supply of the two-way solenoid valve 240. The specific control circuitry and control methods of the proximity switch and the two-way solenoid valve 240 are not limited herein.

[0047] Please refer to Figure 5 , Figure 5 This is a diagram of the hydraulic control principle of a Japanese compactor. The movements of the loader lift cylinder 810 and the loader hook cylinder 820 are both controlled by a reversing valve 830. The loader lowers by energizing the solenoid valve 850, which connects the oil circuit. The loader descends under its own gravity, and the descent speed is controlled by a one-way throttle valve 860. Therefore, the descent of the loader on a Japanese compactor depends on the energization of the solenoid valve 850. A malfunction of the solenoid valve 850 would prevent the loader from descending. The lifting operation of the loader is typically used for unloading operations at landfills or incineration plants. This makes disassembly and maintenance of the loader difficult, impacting the normal operation of the compactor. In addition, the loader lock hook cylinder 820 maintains pressure through the tubular hydraulically controlled one-way valve 840. When the tubular hydraulically controlled one-way valve 840 fails or leaks in the cylinder, or when the multi-way valve has oil cross-linking in the working links, the lock hook will be unhooked. Eliminating this fault requires multiple inspections, which affects work efficiency.

[0048] Please refer to Figure 6 , Figure 6This is a partial hydraulic control schematic diagram of a combined American compression vehicle, in which the loader lifting cylinder 810 and the loader lock hook cylinder 820 of the American compression vehicle are respectively controlled by separate reversing valves 830, and a tubular hydraulically controlled one-way valve 840 is provided in the rod cavity connection of the loader lock hook cylinder 820 to maintain the pressure of the loader lock hook cylinder 820. When the tubular hydraulically controlled one-way valve 840 fails or the cylinder leaks, or when the reversing valve 830 has oil cross-linking in the working connection, the lock hook will be unhooked, and eliminating this fault requires multiple inspections, affecting work efficiency.

[0049] Based on this, in this embodiment, a two-way solenoid ball valve 240 is connected between the fifth reversing valve 520 and the hook cylinder 230. The two-way solenoid ball valve 240 is connected to the rod chamber of the hook cylinder 230 and is normally bidirectionally blocked. The provision of the two-way solenoid ball valve 240 effectively prevents the uncoupling caused by pressure oil leakage from the reversing valve 830 spool, which could cause the tubular hydraulically controlled check valve 840 to open. Furthermore, a pressure tap is provided on the valve body of the two-way solenoid ball valve 240, communicating with the rod chamber of the hook cylinder 230. In the event of abnormal uncoupling, the pressure tap can be used to immediately measure the pressure in the rod chamber of the hook cylinder 230, thereby determining whether there is internal leakage in the cylinder. This reduces the risk of failure and improves fault diagnosis efficiency. Furthermore, the provision of a one-way balancing valve 250 mitigates the problem in conventional garbage compacting trucks where the loader's descent relies on the solenoid valve for power supply, which can prevent the loader from descending if the solenoid valve malfunctions. If the solenoid valve malfunctions, the one-way balancing valve 250 can adjust the opening pressure to slowly lower the loader, improving the safety of the garbage compactor. Furthermore, by connecting the one-way balancing valve 250 to the oil inlet and outlet of the lifting cylinder 220, the lifting cylinder 220 maintains pressure, preventing the loader from suddenly falling and causing a safety accident if the oil circuit malfunctions and pressure is released.

[0050] Therefore, in this embodiment, a two-way electromagnetic ball valve 240 and a one-way balance valve 250 are provided, and the lifting cylinder 220 and the hook cylinder 230 are controlled by the same multi-way valve (fifth reversing valve 520). Figure 5 The hydraulic control system provided in this embodiment improves the loader lifting cylinder 810 into a double-acting lifting cylinder 220 plus a one-way balance valve 250. This improves the disadvantage of the electromagnetic ball valve 850 in Japanese compression vehicles that controls the oil circuit conduction, the loader relies on its own weight to fall, and cannot fall without power. The locking reliability of the loader hook cylinder 820 is guaranteed by the two-way electromagnetic ball valve 240. Compared with traditional American compression vehicles, Figure 6The lifting cylinder 220 and the locking hook cylinder 230 in the hydraulic control system provided in this embodiment are controlled by the same multi-way valve, reducing one multi-way valve and eliminating the tubular hydraulically controlled one-way valve 840 with a rod cavity in the loader locking hook cylinder 820, thereby reducing the risk of failure and enhancing the efficiency of fault diagnosis.

[0051] Please refer to Figure 7 In this embodiment, the first multi-way valve assembly 400 and the second multi-way valve assembly 500 are 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 the problem of conventional multi-way valves, which are assembled from multiple valve plates, resulting in low structural strength and prone to leakage between the multiple valve plates.

[0052] To sum up, the implementation principle of the hydraulic control system of the garbage compression truck and the garbage compression truck provided by the present invention is: by adding an adjustment part 700 to the hydraulic control system, the hydraulic control system of the present invention can be switched between the merging state and the diverting state, so that American and Japanese garbage compression trucks can be used interchangeably and the control principles of the two types of garbage compression trucks are unified. It is suitable for the two mainstream types of garbage compression 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 the present invention, but the scope of protection of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by any technician familiar with this technical field within the technical scope disclosed in the present invention should be covered by the scope of protection of the present invention.

Claims

1. A hydraulic control system for a garbage compacting vehicle, comprising a fuel tank (10), a first oil cylinder group (100) and a second oil cylinder group (200), characterized in that: The hydraulic control system further comprises: A double pump (300), the input end of the double pump being fluidically connected to the oil tank, and the double pump comprising a large pump (310) and a small pump (320); A first multi-way valve group (400) is fluidically connected to the first oil cylinder group (100); A second multi-way valve group (500) is fluidically connected to the second oil cylinder group (200); A first oil inlet passage (610) is fluidically connected to the output end P1 of the large pump (310) and is fluidically connected to the first multi-way valve assembly (400); A second oil inlet passage (620), fluidically connected to the output end P2 of the small pump (320) and fluidically connected to the second multi-way valve assembly (500); An unloading circuit (630) is fluidically connected to the oil tank (10), and the unloading circuit (630) is fluidically connected to both the first multi-way valve group (400) and the second multi-way valve group (500); The regulating member (700) is arranged between the second oil inlet passage (620) and the first oil inlet passage (610), and is used to disconnect the second oil inlet passage (620) from the first oil inlet passage (610) and connect the second oil inlet passage (620) with the unloading circuit (630) so that the hydraulic control system is in a diversion state; and is used to connect the second oil inlet passage (620) to the first oil inlet passage (610) in a one-way manner so that the hydraulic control system is in a converging state.

2. The hydraulic control system of the garbage compactor according to claim 1, characterized in that: The regulating member (700) is a plug, a bridge joint or a first one-way valve; When the hydraulic control system is in the diversion state, the plug, the bridge joint or the first one-way 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 in communication with the unloading circuit (630).

3. The hydraulic control system of the garbage compression truck according to claim 1, characterized in that: The regulating member (700) is a connecting pipe or a second one-way valve; When the hydraulic control system is in the merging state, the connecting pipe or the second one-way 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 garbage compacting truck according to claim 1, characterized in that: The first oil cylinder group (100) includes a push-blade oil cylinder (110), a slide oil cylinder (120) and a scraper oil cylinder (130); the first multi-way valve group (400) includes a first reversing valve (410) fluidically connected to the push-blade oil cylinder (110), a second reversing valve (420) fluidically connected to the slide oil cylinder (120), and a third reversing valve (430) fluidically connected to the scraper oil cylinder (130); The first oil inlet passage (610) is fluidically connected to the third reversing valve (430), the second reversing valve (420), and the first reversing valve (410) in sequence; The unloading circuit (630) is fluidically connected to the first reversing valve (410), the second reversing valve (420), and the third reversing valve (430).

5. The hydraulic control system for a garbage compactor according to claim 1, characterized in that: The second oil cylinder group (200) includes a feeding oil cylinder (210) and a lifting oil cylinder (220), and the second multi-way valve group (500) includes a fourth reversing valve (510) fluidically connected to the feeding oil cylinder (210) and a fifth reversing valve (520) fluidically connected to the lifting oil cylinder (220); The second oil inlet passage (620) is fluidically connected to the fifth reversing valve (520) and the fourth reversing valve (510) in sequence; The unloading circuit (630) is fluidically connected to the fourth reversing valve (510) and the fifth reversing valve (520).

6. The hydraulic control system for a garbage compactor according to claim 5, characterized in that: The second oil cylinder group (200) further comprises a locking hook oil cylinder (230), and a two-way electromagnetic ball valve (240) is connected between the fifth reversing valve (520) and the rod chamber of the locking hook oil cylinder (230).

7. The hydraulic control system for a garbage compactor according to claim 6, characterized in that: The oil port A5 of the fifth reversing valve (520) is communicated with 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 reversing valve (520) is communicated with the rodless chamber of the lifting cylinder (220) and the rodless chamber of the locking hook cylinder (230).

8. The hydraulic control system for a garbage compactor according to claim 6, characterized in that: The rod chamber and the rodless chamber of the lifting oil cylinder (220) are both connected to a one-way balancing valve (250).

9. The hydraulic control system for a garbage compactor according to claim 1, characterized in that: The first multi-way valve assembly (400) and the second multi-way valve assembly (500) are both integrally formed.

10. A garbage compression truck, characterized in that: The hydraulic control system for a garbage compactor comprising any one of claims 1 to 9.

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