Hydraulic system of deicing vehicle and deicing vehicle

Abstract

The embodiment of the present application provides a kind of hydraulic system of deicing vehicle and deicing vehicle, wherein, hydraulic system includes first oil pump, first proportional multi-way valve, first load module, first main oil path, multiple branch oil paths and oil return path, first proportional multi-way valve includes multiple electrically-controlled proportional valve pieces;First load module includes multiple load motors, for corresponding deicing execution element is powered;First main oil path is connected with first oil pump and first proportional multi-way valve, to enable first oil pump can simultaneously deliver hydraulic oil to each proportional valve piece of first proportional multi-way valve;Multiple branch oil paths are connected with first proportional multi-way valve and first load module, to deliver hydraulic oil to each load motor of first load module;Each load motor of first load module is communicated with oil return path.The hydraulic system in the embodiment of the present application can be electrically-controlled to adjust the opening size of proportional valve piece to adapt to different load power demand, reduce power loss, reduce the heat generated in work.

Description

TECHNICAL FIELD

[0001] The embodiment of the application relates to the technical field of deicing vehicles, and particularly relates to a hydraulic system of a deicing vehicle and the deicing vehicle. BACKGROUND

[0002] In cold weather conditions, icing on the surface of an aircraft can seriously affect the aerodynamic effect and operability of the aircraft, and cause a major hidden danger to flight safety. Therefore, deicing and anti-icing operations on the surface of the aircraft on the ground are important links in aircraft ground maintenance operations.

[0003] At present, deicing operations on the aircraft are mainly performed by deicing vehicles.

[0004] In the deicing vehicle, a hydraulic system needs to be formed by a hydraulic pump, a hydraulic motor and a hydraulic actuator to drive load devices such as a high-altitude operation platform and a spraying device.

[0005] In the related art, a cartridge valve is used to control the load motor of the deicing actuator, and the fixed orifice of the cartridge valve often needs to be adjusted. For example, when the deicing vehicle is debugged, the spraying device sprays water, but after leaving the factory, the deicing vehicle sprays anti-icing liquid mixed with water, and the loads of the two are different, so the fixed orifice needs to be adjusted again before being put into formal use; when the volumetric efficiency of the pump and the motor changes, the fixed orifice needs to be adjusted again. SUMMARY

[0006] Therefore, the embodiments of the application aim to provide a hydraulic system of a deicing vehicle and the deicing vehicle to facilitate control of the flow supply of the load motor of the deicing actuator.

[0007] To achieve the above-mentioned purpose, the technical scheme of the embodiments of the application is as follows:

[0008] The embodiment of the application provides a hydraulic system of a deicing vehicle, the deicing vehicle comprising a plurality of deicing actuators, and the hydraulic system comprising:

[0009] a first oil pump;

[0010] a first proportional multi-way valve comprising a plurality of electrically-controlled proportional valve plates;

[0011] a first load module comprising a plurality of load motors for providing power for the corresponding deicing actuators;

[0012] a first main oil path connecting the first oil pump and the first proportional multi-way valve, so that the first oil pump can simultaneously deliver hydraulic oil to each proportional valve plate of the first proportional multi-way valve;

[0013] a plurality of branch oil paths, which are communicated with the first proportional multi-way valve and the first load module, to deliver hydraulic oil to each of the load motors of the first load module;

[0014] a return oil path, which is communicated with each of the load motors of the first load module.

[0015] In some embodiments, the plurality of load motors of the first load module are respectively a de-icing motor, an anti-icing motor, a fuel motor and a fan motor, and the plurality of branch oil paths are divided into a first branch oil path, a second branch oil path and a third branch oil path;

[0016] The first branch oil path is communicated with the corresponding proportional valve piece to deliver hydraulic oil to the de-icing motor, the second branch oil path is communicated with the corresponding proportional valve piece to deliver hydraulic oil to the anti-icing motor, and the third branch oil path is communicated with the corresponding proportional valve piece to deliver hydraulic oil to the fuel motor and the fan motor in series.

[0017] In some embodiments, the third branch oil path includes a first sub-oil path, a second sub-oil path, a third sub-oil path and a fourth sub-oil path, the first sub-oil path is communicated with the corresponding proportional valve piece to deliver hydraulic oil to one of the fuel motor and the fan motor, the second sub-oil path is in series with the fuel motor and the fan motor, the third sub-oil path is communicated with the first sub-oil path and the second sub-oil path, and the fourth sub-oil path is communicated with the second sub-oil path and the return oil path.

[0018] The hydraulic system includes a first one-way valve, a first on-off valve and a second on-off valve, the first one-way valve is arranged on the second sub-oil path to allow hydraulic oil to flow in one direction between the fuel motor and the fan motor, the first on-off valve is arranged on the third sub-oil path to selectively open or close the third sub-oil path, and the second on-off valve is arranged on the fourth sub-oil path to selectively open or close the fourth sub-oil path.

[0019] In some embodiments, the hydraulic system includes a first overflow valve, which is arranged on the fourth sub-oil path in parallel with the second on-off valve.

[0020] In some embodiments, the hydraulic system includes a second one-way valve, which is arranged in parallel with the de-icing motor; and / or,

[0021] The hydraulic system includes a third one-way valve, which is arranged in parallel with the fan motor.

[0022] In some embodiments, the hydraulic system includes:

[0023] a second oil pump;

[0024] a second proportional multi-way valve comprising a plurality of electrically controlled proportional spools;

[0025] a second load module comprising a plurality of actuating elements for driving the boom of the de-icing vehicle;

[0026] a second main oil passage connecting the second oil pump and the second proportional multi-way valve, so that the second oil pump can simultaneously deliver hydraulic oil to each proportional spool of the second proportional multi-way valve;

[0027] an overflow module connecting each proportional spool of the second proportional multi-way valve, for overflow unloading of the second load module.

[0028] In some embodiments, the overflow module comprises a plurality of third on-off valves, each proportional spool of the second proportional multi-way valve being connected to at least one third on-off valve, so as to selectively overflow unload the proportional spool of the second proportional multi-way valve.

[0029] In some embodiments, the hydraulic system comprises:

[0030] a second oil pump;

[0031] a second proportional multi-way valve comprising a plurality of electrically controlled proportional spools;

[0032] a second load module comprising a plurality of actuating elements for driving the boom of the de-icing vehicle;

[0033] a second main oil passage connecting the second oil pump and the second proportional multi-way valve, so that the second oil pump can simultaneously deliver hydraulic oil to each proportional spool of the second proportional multi-way valve;

[0034] wherein the second proportional multi-way valve and the first proportional multi-way valve are integrally arranged to form a proportional multi-way valve assembly, and the first main oil passage and the second main oil passage converge to deliver hydraulic oil to the proportional multi-way valve assembly.

[0035] In some embodiments, the hydraulic system comprises a back pressure valve arranged in the return oil passage, to prevent the return oil passage from supplying oil to the first load module.

[0036] The embodiments of the present application also provide a de-icing vehicle comprising:

[0037] a plurality of de-icing actuating elements for spraying liquid capable of de-icing onto objects to be de-iced;

[0038] the hydraulic system of any one of the foregoing embodiments, the first load module being drivingly connected to the de-icing actuating elements, to drive the de-icing actuating elements to work.

[0039] The hydraulic system in the embodiment of the present application can adjust the opening size of the proportional valve in an electric control manner, and then control the flow of the hydraulic oil delivered to the load motor to adapt to different load requirements, so that the hydraulic system in the embodiment of the present application can realize integrated control based on load changes together with the related electric control system, by loading the corresponding control parameters in the software program of the electric control system under different working conditions, for example, different opening sizes of the proportional valve under different working conditions, the displacement of the first oil pump and the opening size of the proportional valve are adaptively adapted to the load power requirement, thereby avoiding the problem of re-calibration and debugging after each change of working condition, simplifying the adjustment steps, and improving the response speed of the hydraulic system; the number of proportional valves can be selected as needed according to different load motors, the modular configuration of the first proportional multi-way valve is realized, the installation space is saved, and the disassembly and subsequent maintenance and replacement are facilitated; the hydraulic oil output to the first load module is uniformly controlled by the first oil pump and the first proportional multi-way valve, so that the output oil quantity of the first oil pump can be adaptively changed according to the change of the total demand of the first load module, thereby reducing the power loss of the hydraulic system, improving the power utilization efficiency, and reducing the heat generated by the hydraulic system during operation. BRIEF DESCRIPTION OF DRAWINGS

[0040] Figure 1 FIG. 1 is a schematic diagram of the hydraulic system of the deicing vehicle in an embodiment of the present application;

[0041] Figure 2 FIG. 2 is a schematic diagram of the first load module and the branch oil path in the embodiment of the present application. Figure 1

[0042] BRIEF DESCRIPTION OF DRAWINGS

[0043] First oil pump 10; first proportional multi-way valve 20; first load module 30; deicing motor 31; second one-way valve 311; anti-icing motor 32; fuel motor 33; fan motor 34; first one-way valve 35; first on-off valve 36; second on-off valve 37; first overflow valve 38; third one-way valve 39; first main oil path 40; second main oil path 41; branch oil path 50; first branch oil path 51; second branch oil path 52; third branch oil path 53; first sub-oil path 531; second sub-oil path 532; third sub-oil path 533; fourth sub-oil path 534; oil return path 60; back pressure valve 61; second oil pump 70; second proportional multi-way valve 80; second load module 90; overflow module 91; third on-off valve 911; first pressure sensor 92; second pressure sensor 93 DETAILED DESCRIPTION

[0044] It should be noted that the embodiments in the present application and the technical features in the embodiments can be combined with each other without conflict, and the detailed description in the specific embodiments should be understood as the explanation and description of the purpose of the present application, and should not be regarded as improper limitation of the present application.​

[0045] The hydraulic system of the deicing vehicle is used for driving the deicing execution elements to work.

[0046] Referring to Figure 1 The hydraulic system comprises a first oil pump 10, a first proportional multi-way valve 20, a first load module 30, a first main oil path 40, a plurality of branch oil paths 50 and an oil return path 60.

[0047] The first load module 30 comprises a plurality of load motors, which are used for providing power for corresponding deicing execution elements to drive the deicing execution elements to work.

[0048] The specific corresponding relationship between the load motor and the deicing execution element is not limited, that is, one load motor can drive one deicing execution element to work, or multiple load motors can drive one deicing execution element to work, or one load motor can drive multiple deicing execution elements to work. The specific corresponding relationship is selected according to the load demand between the load motor and the corresponding deicing execution element, safety redundancy and other factors.

[0049] The first main oil path 40 is connected between the first oil pump 10 and the first proportional multi-way valve 20 to provide hydraulic oil for the first proportional multi-way valve 20. The first proportional multi-way valve 20 comprises a plurality of electrically controlled proportional valve pieces, the first oil pump 10 can simultaneously deliver hydraulic oil to each proportional valve piece of the first proportional multi-way valve 20, and the plurality of branch oil paths 50 are connected between the first proportional multi-way valve 20 and the first load module 30 to deliver hydraulic oil to each load motor of the first load module 30. That is, the hydraulic oil output by the first oil pump 10 is input into the first proportional multi-way valve 20 through the first main oil path 40 and is distributed to each proportional valve piece, each proportional valve piece outputs hydraulic oil with a corresponding flow rate to the corresponding load motor through the corresponding branch oil path 50 according to the working demand, so as to control the output power of each load motor, thereby achieving the purpose of controlling the corresponding deicing execution element.

[0050] The first proportional multi-way valve 20 can be a load-sensitive proportional multi-way valve, so that the proportional valve pieces in the first proportional multi-way valve 20 can control the corresponding load motors according to the different load demands of different deicing execution elements.

[0051] The specific type of the first oil pump 10 is not limited, for example, a plunger pump.

[0052] The first oil pump 10 can be an electrically controlled load-sensitive variable pump, which can adjust its displacement according to the total working load power demand of the first load module 30 to adapt to the total demand of the first load module 30 in different load states.

[0053] Each load motor of the first load module 30 is communicated with the oil return path 60 to recover hydraulic oil.

[0054] The hydraulic system in the embodiment of the present application can adjust the opening size of the proportional valve disc in an electric control manner, and then regulate the flow of the hydraulic oil delivered to the load motor to adapt to different load requirements, so that the hydraulic system in the embodiment of the present application can realize integrated control based on load change together with the related electric control system. By loading the corresponding control parameters in the software program of the electric control system under different working conditions, for example, different opening sizes of the proportional valve disc under different working conditions, the displacement of the first oil pump 10 and the opening size of the proportional valve disc are adaptively matched with the load power requirement, thereby avoiding the problem of re-calibration and debugging after each change of working condition, simplifying the adjustment steps, and improving the response speed of the hydraulic system. The number of proportional valve discs can be selected as needed according to different load motors to realize modular configuration of the first proportional multi-way valve 20, save installation space, and facilitate disassembly, assembly and subsequent maintenance and replacement. The hydraulic oil output to the first load module 30 is uniformly controlled by the first oil pump 10 and the first proportional multi-way valve 20, which is convenient for adaptively changing the output oil volume of the first oil pump 10 according to the change of the total demand of the first load module 30, thereby reducing the power loss of the hydraulic system, improving the power utilization efficiency, and reducing the heat generated by the hydraulic system during operation.

[0055] It should be noted that the specific selection method, oil path arrangement, number configuration, etc. of the valve blocks such as the reversing valve, the overflow valve, and the shuttle valve involved in each proportional valve disc of the first proportional multi-way valve 20 have been applied in related technologies, and are not described here.

[0056] It should be noted that the opening of each electric control proportional valve disc is controlled by the load in an electric control manner to meet the power requirement that the hydraulic oil flow output by each proportional valve disc meets the load demand. The composition, connection relationship, electric control algorithm, etc. of the related electric control system have been applied in related technologies, and are not described here.

[0057] It can be understood that the LS port of each proportional valve disc of the first proportional multi-way valve 20 is provided with a pressure sensor to respectively acquire the hydraulic oil pressure in each proportional valve disc. The outlet of the first oil pump 10 is provided with a second pressure sensor 93 to acquire the hydraulic oil pressure output by the first oil pump 10. By comparing the hydraulic oil pressure in each proportional valve disc and the hydraulic oil pressure output by the first oil pump 10, a reference is provided for the adjustment of the output flow of the first oil pump 10, thereby reducing the power loss and heat generation of the hydraulic system, and achieving the purpose of energy saving.

[0058] It can be understood that, due to different loads of the load motors, the required flow of hydraulic oil into each proportional valve piece is different, and the flow of hydraulic oil delivered by the first oil pump 10 to the first proportional multi-way valve 20 is not less than the sum of the required flows of hydraulic oil in each proportional valve piece.

[0059] In some embodiments, referring to Figure 1 , the hydraulic system further comprises an oil tank, the first oil pump 10 draws hydraulic oil from the oil tank, and the hydraulic oil in the return flow path converges returns to the oil tank, so that the hydraulic oil can be recycled in the hydraulic system.

[0060] The specific type of the load motor in the first load module 30 is not limited, which can be a fixed displacement motor or a variable displacement motor, and is determined according to the specific deicing execution element type.

[0061] The specific function of the load motor is not limited, for example, the plurality of load motors are respectively deicing motor 31, anti-icing motor 32, fuel motor 33 and fan motor 34, wherein the deicing motor 31 is used to drive the deicing liquid pump, the anti-icing motor 32 is used to drive the anti-icing liquid pump, the fuel motor 33 is used to drive the fuel pump of the heating device, and the fan motor 34 is used to drive the fan of the heating device.

[0062] It can be understood that the fuel motor 33, the fan motor 34, the anti-icing motor 32 and the deicing motor 31 are respectively provided with a speed sensor and other sensors, the required flow of each load motor is obtained through calculation of the electronic control system, and is compared with the output flow of each proportional valve piece in the electronic control of the first proportional multi-way valve 20, so as to realize closed-loop control between the required flow of each load motor and the output flow of each proportional valve piece, continuously correct the output flow of each proportional valve piece through electronic control, so as to keep the speed of each load motor stable, meet the output power requirement, improve the stability of the hydraulic system, and reduce heat generation.

[0063] It can be understood that the working pressures of the load motors are different, and the pressure values of the hydraulic oil delivered by the first oil pump 10 to each proportional valve piece through the first main oil path 40 are the same, therefore, it is necessary to reasonably arrange the load motors to adjust the pressure difference of the hydraulic oil between the branch oil paths 50, so as to meet the flow requirement of each load motor, thereby reducing the power loss caused by the proportional valve piece regulating the flow of hydraulic oil.

[0064] Exemplarily, referring to Figure 2 , the branch oil path 50 is divided into a first branch oil path 51, a second branch oil path 52 and a third branch oil path 53, the first branch oil path 51 communicates the corresponding proportional valve piece to deliver hydraulic oil to the deicing motor 31, the second branch oil path 52 communicates the corresponding proportional valve piece to deliver hydraulic oil to the anti-icing motor 32, and the third branch oil path 53 communicates the corresponding proportional valve piece to deliver hydraulic oil to the series-connected fuel motor 33 and fan motor 34.

[0065] For example, if the required hydraulic oil pressure for the de-icing motor 31 is 13 MPa (Megapascal), the hydraulic oil pressure delivered by the first oil passage 51 is not less than 13 MPa; if the required hydraulic oil pressure for the anti-icing motor 32 is 12 MPa (Megapascal), the hydraulic oil pressure delivered by the second oil passage 52 is not less than 12 MPa; if one of the required hydraulic oil pressure for the fuel motor 33 and the required hydraulic oil pressure for the fan motor 34 is 5 MPa and the other is 6 MPa, the hydraulic oil pressure delivered by the third oil passage 53 is not less than 11 MPa, so that the required hydraulic oil pressure of the load motors distributed on the first oil passage 51, the second oil passage 52 and the third oil passage 53 is close to each other.

[0066] By connecting the fuel motor 33 and the fan motor 34 in series, the required hydraulic oil pressure of the load motors distributed on the first oil passage 51, the second oil passage 52 and the third oil passage 53 is close to each other, so that the power loss caused by the large pressure difference between the required pressure of the load motors and the output pressure of the first oil pump 10 is reduced, and the heat generation of the system is further reduced, and the energy utilization efficiency is improved.

[0067] It can be understood that the two fuel motor 33 and the fan motor 34 which need to be connected in series can be controlled respectively.

[0068] Specifically, referring to Figure 2 , the third oil passage 53 includes a first sub-oil passage 531, a second sub-oil passage 532, a third sub-oil passage 533 and a fourth sub-oil passage 534, the first sub-oil passage 531 communicates the corresponding proportional valve piece to deliver hydraulic oil to the fuel motor 33, the second sub-oil passage 532 connects the fuel motor 33 and the fan motor 34 in series, the third sub-oil passage 533 communicates the first sub-oil passage 531 and the second sub-oil passage 532, and the fourth sub-oil passage 534 communicates the second sub-oil passage 532 and the oil return passage 60; the hydraulic system includes a first switch valve 36 and a second switch valve 37, the first switch valve 36 is arranged on the third sub-oil passage 533 to selectively open or close the third sub-oil passage 533, and the second switch valve 37 is arranged on the fourth sub-oil passage 534 to selectively open or close the fourth sub-oil passage 534. That is, the fuel motor 33 is connected in parallel with the first switch valve 36, and the fan motor 34 is connected in parallel with the second switch valve 37.

[0069] If both the fuel motor 33 and the fan motor 34 need to be in working state, the first switch valve 36 closes the third sub-oil passage 533, and the second switch valve 37 closes the fourth sub-oil passage 534, so that the hydraulic oil enters the fuel motor 33 through the first sub-oil passage 531, and then enters the fan motor 34 through the second sub-oil passage 532, thereby driving both to work at the same time.

[0070] If one of the fuel motor 33 and the blower motor 34 needs to be in operation, two cases are considered. One case is that the fuel motor 33 needs to be driven alone, in which case the first switch valve 36 is opened and the second switch valve 37 is closed, so that the hydraulic oil flows from the first sub-oil passage 531 through the fuel motor 33 and then into the fourth sub-oil passage 534. The other case is that the blower motor 34 needs to be driven alone, in which case the first switch valve 36 is closed and the second switch valve 37 is opened, so that the hydraulic oil flows through the second sub-oil passage 533 and then into the blower motor 34.

[0071] As described above, it is achieved to control either of the fuel motor 33 and the blower motor 34 to be in operation, so that the flexibility of use of the hydraulic system is improved.

[0072] The specific way in which the first switch valve 36 and the second switch valve 37 are opened or closed is not limited, and can be mechanical control or electrical control.

[0073] In some embodiments, referring to Figure 2 , the hydraulic system comprises a first check valve 35 arranged on the second sub-oil passage 532, so that the hydraulic oil flows in one direction between the fuel motor 33 and the blower motor 34, thereby reducing the backflow of the hydraulic oil and the adverse effect on the fuel motor 33.

[0074] It can be understood that, referring to Figure 2 , the communication position of the third sub-oil passage 533 with the second sub-oil passage 532 and the communication position of the fourth sub-oil passage 534 with the second sub-oil passage 532 are both downstream of the first check valve 35 along the flow direction allowed by the first check valve 35, so that the hydraulic oil in the second sub-oil passage 532 cannot impact the fuel motor 33 when the fuel motor 33 is in a stopped state.

[0075] It can be understood that, it is necessary to reduce the overpressure of the oil passage and the adverse effect on the fuel motor 33 or the blower motor 34.

[0076] Exemplarily, referring to Figure 2 , the hydraulic system comprises a first overflow valve 38 arranged on the fourth sub-oil passage 534 in parallel with the second switch valve 37. In this way, when the oil pressure on the input side of the blower motor 34 is too high, the first overflow valve 38 is opened under the action of the oil pressure, so that part of the hydraulic oil in the second sub-oil passage 532 directly flows into the oil return passage 60, thereby achieving the purpose of reducing the oil pressure and limiting the speed of the blower motor 34. It can be understood that, it is necessary to suppress the suction phenomenon generated by each load motor when it is running at high speed.

[0077] In some embodiments, referring to Figure 2The hydraulic system comprises a second one-way valve 311 which is arranged in parallel with the deicing motor 31. When the deicing motor 31 is running at a high speed and a vacuum cavity is generated inside the deicing motor 31, the second one-way valve 311 is opened under the action of a pressure difference, so that the hydraulic oil on the oil outlet side of the deicing motor 31 can flow back to the oil inlet side of the deicing motor 31, thereby playing a role of oil supplementing, so as to inhibit the probability of air suction of the deicing motor 31, reduce the vibration and noise of the deicing motor 31 during operation, reduce the probability of cavitation of the deicing motor 31, and improve the service life of the deicing motor 31.

[0078] In some embodiments, referring to Figure 2 The hydraulic system comprises a third one-way valve 39 which is arranged in parallel with the fan motor 34. When the fan motor 34 is running at a high speed and a vacuum cavity is generated inside the fan motor 34, the third one-way valve 39 is opened under the action of a pressure difference, so that the hydraulic oil on the oil outlet side of the fan motor 34 can flow back to the oil inlet side of the fan motor 34, thereby playing a role of oil supplementing, so as to inhibit the probability of air suction of the fan motor 34, reduce the vibration and noise of the fan motor 34 during operation, reduce the probability of cavitation of the fan motor 34, and improve the service life of the fan motor 34.

[0079] It should be noted that, as an alternative embodiment, the positions of the fuel motor 33 and the fan motor 34 can be interchanged in the above embodiments.

[0080] It can be understood that the hydraulic system can also drive other executing elements in addition to the deicing executing elements in the deicing vehicle.

[0081] For example, referring to Figure 1 The hydraulic system further comprises a second oil pump 70, a second proportional multi-way valve 80, a second load module 90 and a second main oil line 41. The second proportional multi-way valve 80 comprises a plurality of proportional valve pieces, the second load module 90 comprises a plurality of executing elements for driving the arm support movement of the deicing vehicle, and the second main oil line 41 is connected between the second oil pump 70 and the second proportional multi-way valve 80, so that the second oil pump 70 can simultaneously deliver hydraulic oil to each proportional valve piece of the second proportional multi-way valve 80. The hydraulic oil output by the second oil pump 70 is input into the second proportional multi-way valve 80 through the second main oil line 41 and is distributed to each proportional valve piece, and each proportional valve piece outputs hydraulic oil with a corresponding required flow rate to the executing elements in the corresponding second load module 90 according to the work requirement.

[0082] It can be understood that the executing elements in each second load module 90 are different, the working conditions are different, and the required hydraulic oil flow rates are different, and therefore the hydraulic oil flow rates output by each proportional valve piece in the second proportional multi-way valve 80 to the executing elements in the corresponding second load module 90 are also different.

[0083] Each proportional spool in the second proportional multi-way valve 80 can adjust the flow of hydraulic oil delivered according to the load of the corresponding actuating element, so as to adaptively meet the varying flow demand of each actuating element, effectively reducing the power waste caused by pressure build-up for limiting the flow delivered to the actuating element, reducing the power loss of the hydraulic system, and reducing the heat generated by the hydraulic system during operation; the second proportional multi-way valve 80 is modularly composed of multiple proportional spools, facilitating disassembly and subsequent maintenance and replacement.

[0084] The specific type of the second oil pump 70 is not limited, such as a fixed displacement pump.

[0085] The specific type of the actuating element included in the second load module 90 is not limited, such as a hydraulic cylinder, a hydraulic motor, etc., wherein the hydraulic cylinder can be used to drive the arm frame to vary the amplitude and extend or retract, and the hydraulic motor can be used to drive the arm frame to rotate.

[0086] The specific number of actuating elements is not limited, which can be one or multiple.

[0087] It can be understood that the movement of the arm frame needs to be limited by the hydraulic system to reduce the probability of collision of the arm frame.

[0088] Exemplarily, referring to Figure 1 , the hydraulic system includes an overflow module 91, which is communicated with each proportional spool of the second proportional multi-way valve 80, for overflow unloading of the second load module 90.

[0089] In the case that the arm frame moves to a preset safe position or collides, the overflow module 91 can overflow unload the second load module 90, so that the actuating elements in the second load module 90 lose pressure and stop moving, thereby reducing the risk of collision of the arm frame or reducing the probability of further damage of the arm frame, and improving the safety of the de-icing vehicle.

[0090] The specific manner of overflow implemented by the overflow module 91 is not limited.

[0091] Exemplarily, referring to Figure 1 , the overflow module 91 includes multiple third on-off valves 911, each proportional spool of the second proportional multi-way valve 80 is communicated with at least one third on-off valve 911, so as to selectively overflow unload the proportional spool of the second proportional multi-way valve 80.

[0092] In the case that the third switch valve 911 is closed, the proportional valve disc delivers hydraulic oil to the corresponding actuator in the second load module 90; in the case that the third switch valve 911 is opened, the hydraulic oil in the proportional valve disc flows out through the third switch valve 911, so that the corresponding actuator in the second load module 90 loses power and stops. By controlling the opening and closing of different third switch valves 911, the shutdown control of specific actuators in the second load module 90 is realized, the flexibility of the hydraulic system control is improved, and the risk of damage to other actuators that do not need to stop due to the impact caused by stopping is avoided.

[0093] It can be understood that the overflow module 91 can be in communication with the oil tank or the oil return passage 60, so that the overflow of the overflow module 91 can continue to circulate in the hydraulic system.

[0094] The control mode of the third switch valve 911 is not limited, which can be mechanical control or electrical control.

[0095] In some embodiments provided with the first proportional multi-way valve 20 and the second proportional multi-way valve 80, referring to Figure 1 , the second proportional multi-way valve 80 and the first proportional multi-way valve 20 are integrally arranged to form a proportional multi-way valve assembly, that is, a plurality of proportional valve discs form the proportional multi-way valve assembly, wherein a part of the proportional valve discs form the first proportional multi-way valve 20, and another part of the proportional valve discs form the second proportional multi-way valve 80. The first main oil passage 40 and the second main oil passage 41 converge to deliver hydraulic oil to the proportional multi-way valve assembly, that is, the power required by the first load module 30 and the second load module 90 is provided by the first oil pump 10 and the second oil pump 70, so as to realize a wider power output adjustment range of the first load module 30 and the second load module 90, and at the same time, the first oil pump 10 and the second oil pump 70 complement each other, so that in the case of high load demand, the first oil pump 10 can provide additional power to the second load module 90 through the second proportional multi-way valve 80, or the second oil pump 70 can provide additional power to the first load module 30 through the first proportional multi-way valve 20, thereby improving the safety redundancy of the hydraulic system without the need for an additional emergency pump.

[0096] Referring to Figure 1 , each proportional valve disc in the proportional multi-way valve assembly has a total LS port, a first pressure sensor 92 is arranged at the LS port, so as to obtain the maximum hydraulic oil pressure of the proportional multi-way valve assembly, and by cooperating with a second pressure sensor 93 arranged at the oil outlet of the first oil pump 10, the pressure difference between the pressure obtained by the first pressure sensor 92 and the pressure of the second pressure sensor 93 is obtained, and the opening size of each proportional valve disc is adjusted according to the change of the pressure difference to realize the adjustment of the flow, so as to meet the flow demand and reduce the power loss.

[0097] It can be understood that it is necessary to avoid the hydraulic oil in the oil return path 60 directly flowing into the load motor.

[0098] In some embodiments, referring to Figure 1 The hydraulic system comprises a back pressure valve 61 arranged in the oil return path 60 to prevent the oil return path 60 from supplying oil to the first load module 30, thereby avoiding the hydraulic oil being directly sucked from the oil return path 60 due to air suction during high-speed operation of the load motor.

[0099] The embodiments of the present application also provide an ice-melting vehicle, which comprises a plurality of ice-melting execution elements and the hydraulic system of any one of the foregoing embodiments, the first load module 30 being drivingly connected with the ice-melting execution elements to drive the ice-melting execution elements to work.

[0100] The ice-melting execution elements include fuel pumps and fan pumps of heating devices, and ice-prevention liquid pumps and de-icing liquid pumps for conveying medium.

[0101] In some embodiments, the ice-melting vehicle further comprises an arm support, and the second load module 90 in the hydraulic system is used to drive the arm support to move, so as to improve the ice-melting range and expand the applicable working conditions of the ice-melting vehicle.

[0102] The various embodiments / implementation manners provided in the present application can be combined with each other without contradiction.

[0103] The above merely describes the preferred embodiments of the present application and is not used to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A hydraulic system of a deicing vehicle including a plurality of deicing execution elements, characterized by, The hydraulic system comprises: a first oil pump; a first proportional multi-way valve comprising a plurality of electrically controlled proportional valve spools; a first load module comprising a plurality of load motors for powering corresponding de-icing execution elements; a first main oil passage connecting the first oil pump and the first proportional multi-way valve, so that the first oil pump can simultaneously deliver hydraulic oil to each proportional valve spool of the first proportional multi-way valve; a plurality of branch oil passages connecting the first proportional multi-way valve and the first load module, so as to deliver hydraulic oil to each load motor of the first load module; a return oil passage, each load motor of the first load module being in communication with the return oil passage; the plurality of load motors of the first load module are respectively de-icing motors, anti-icing motors, fuel motors and fan motors, and the branch oil passages are divided into first, second and third branch oil passages; the first branch oil passage delivers hydraulic oil to the de-icing motor through the corresponding proportional valve spool, the second branch oil passage delivers hydraulic oil to the anti-icing motor through the corresponding proportional valve spool, and the third branch oil passage delivers hydraulic oil to the series-connected fuel motor and fan motor through the corresponding proportional valve spool; the third branch oil passage comprises first, second, third and fourth sub-oil passages, the first sub-oil passage delivers hydraulic oil to one of the fuel motor and the fan motor through the corresponding proportional valve spool, the second sub-oil passage series-connects the fuel motor and the fan motor, the third sub-oil passage connects the first sub-oil passage and the second sub-oil passage, and the fourth sub-oil passage connects the second sub-oil passage and the return oil passage; the hydraulic system comprises a first check valve, a first on-off valve and a second on-off valve, the first check valve is arranged on the second sub-oil passage to allow hydraulic oil to flow unidirectionally between the fuel motor and the fan motor, the first on-off valve is arranged on the third sub-oil passage to selectively open or close the third sub-oil passage, and the second on-off valve is arranged on the fourth sub-oil passage to selectively open or close the fourth sub-oil passage.

2. The hydraulic system of claim 1, wherein, The hydraulic system comprises a first overflow valve arranged in parallel with the second on-off valve on the fourth sub-oil passage.

3. The hydraulic system of claim 1, wherein, The hydraulic system comprises a second check valve arranged in parallel with the de-icing motor; and / or The hydraulic system comprises a third check valve arranged in parallel with the fan motor.

4. The hydraulic system of claim 1, wherein, The hydraulic system comprises: a second oil pump; a second proportional multi-way valve comprising a plurality of electrically controlled proportional valve spools; a second load module comprising a plurality of execution elements for driving the boom of the de-icing vehicle to move; a second main oil passage connecting the second oil pump and the second proportional multi-way valve, so that the second oil pump can simultaneously deliver hydraulic oil to each proportional valve spool of the second proportional multi-way valve; an overflow module connecting each proportional valve spool of the second proportional multi-way valve for overflow unloading of the second load module.

5. The hydraulic system of claim 4, wherein, The overflow module includes a plurality of third on-off valves, each proportional spool of the second proportional multi-way valve is communicated with at least one third on-off valve to selectively overflow unload the proportional spool of the second proportional multi-way valve.

6. The hydraulic system of claim 1, wherein, The hydraulic system includes: a second oil pump; a second proportional multi-way valve including a plurality of electrically controlled proportional spools; a second load module including a plurality of actuating elements for driving the boom of the de-icing vehicle to move; a second main oil line communicated between the second oil pump and the second proportional multi-way valve to enable the second oil pump to simultaneously deliver hydraulic oil to each proportional spool of the second proportional multi-way valve; wherein the second proportional multi-way valve and the first proportional multi-way valve are integrally arranged to form a proportional multi-way valve assembly, and the first main oil line and the second main oil line are merged to deliver hydraulic oil to the proportional multi-way valve assembly.

7. The hydraulic system of claim 1, wherein, The hydraulic system includes a back pressure valve arranged in the oil return line to prevent the oil return line from supplying oil to the first load module.

8. A de-icing vehicle, characterized in that The hydraulic system includes: a plurality of de-icing actuating elements for spraying liquid capable of de-icing to the object to be de-iced; According to any one of claims 1-7, the first load module is drivingly connected with the de-icing actuating elements to drive the de-icing actuating elements to work.

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