Hydraulic system of deep ploughing machine

Abstract

The utility model discloses a hydraulic system of a deep ploughing machine, which belongs to the technical field of deep ploughing machines, and comprises a control part hydraulic system, a hydraulic walking part and an auxiliary control hydraulic part, the control part hydraulic system comprises a working gear pump, the working gear pump is connected with a priority valve, and a CF port of the priority valve is connected with a steering oil cylinder; the port EF is respectively connected with a turnover oil cylinder and a lifting oil cylinder through a turnover multi-way reversing valve and a lifting multi-way reversing valve; the walking part comprises a walking variable pump; the walking variable pump is connected with a driving mechanism through a variable motor; the high-low gear conversion part comprises an auxiliary gear pump, the auxiliary gear pump is connected with a gear shifting oil cylinder and a clutch oil cylinder, and the clutch oil cylinder controls a clutch between the working assembly and the flywheel end of the engine. The high-low gear conversion function of the driving mechanism and the clutch control function of a clutch of the working assembly are achieved by controlling the two three-position four-way valves; the overturning function and the vertical lifting function of the working assembly of the deep ploughing machine are controlled through the two multi-way reversing valves respectively, and a control system is simpler and more convenient.

Description

Technical Field

[0001] The utility model belongs to the technical field of subsoilers, and particularly relates to a hydraulic system for a subsoiler. Background Technique

[0002] The statements in this part only provide background technical information related to the utility model, and do not necessarily constitute prior art.

[0003] A subsoiler is a device used for deep tillage and loosening of soil. By driving the working components to flip, the spiral knives of the working components penetrate into the soil layer and rotate to stir the soil layer, and at the same time, the subsoiler is driven to move, so as to realize the deep tillage operation of the land.

[0004] The traditional subsoiler is equipped with two engines. One engine independently controls the traveling function of the subsoiler, and the other engine independently controls the rotation of the spiral knives of the working components and the flipping function of the working components. This way of providing power by two engines will first cause waste of power. Secondly, because the traveling function and the working function are not related to each other, this independent control causes the operator to need to operate two separate control systems when driving the subsoiler for operation, resulting in a complex control system, increasing the work burden of the operator, and prone to operation errors. Content of the Utility Model

[0005] In view of the above problems, the utility model provides a hydraulic system for a subsoiler, including a control part hydraulic system, a hydraulic traveling part, and an auxiliary control hydraulic part. It is powered by one engine, associates the traveling function with the working function, and controlling two three-position four-way valves of the auxiliary control hydraulic part can realize the high and low gear conversion function of the driving mechanism and the clutch engagement and disengagement control function of the working components; the flipping function and the vertical lifting function of the working components of the subsoiler are respectively controlled by two multi-way directional control valves of the control part hydraulic system. The control system is simple, reduces the work burden of the operator, and is not prone to operation errors.

[0006] To achieve the above object, the utility model adopts the following technical solutions:

[0007] A deep tillage machine hydraulic system, including a control part hydraulic system, a hydraulic walking part, and an auxiliary control hydraulic part, uses one engine to provide mechanical power; the control part hydraulic system includes a working gear pump, one end of the working gear pump is connected to the fuel tank, and the other end is connected to the P port of the priority valve. The CF port of the priority valve is connected to the steering cylinder, and the EF port of the priority valve is respectively connected to the tipping multi-way directional control valve and the lifting multi-way directional control valve. The tipping multi-way directional control valve is connected to the tipping cylinder, and the lifting multi-way directional control valve is connected to the lifting cylinder; the walking part includes a walking variable pump, one end of the walking variable pump is connected to the liquid replenishing tank, and the other end is connected to the variable motor. The variable motor is connected to the gearbox of the driving mechanism; the auxiliary control hydraulic part includes an auxiliary gear pump, and the auxiliary gear pump is connected to the shift cylinder and the clutch cylinder. The clutch cylinder controls the clutch between the engine flywheel end and the working component; the shift cylinder controls the gearbox of the driving mechanism.

[0008] Preferably, a first oil suction filter is provided between the working gear pump and the fuel tank; a first filter is connected between the working gear pump and the priority valve.

[0009] Preferably, a tipping hydraulic lock is connected between the tipping multi-way directional control valve and the tipping cylinder; a lifting hydraulic lock is connected between the lifting multi-way directional control valve and the lifting cylinder.

[0010] Preferably, the T ports of the tipping multi-way directional control valve, the lifting multi-way directional control valve, and the priority valve are connected to the fuel tank through a first cooler.

[0011] Preferably, a hydraulic steering gear is connected between the CF port of the priority valve and the steering cylinder.

[0012] Preferably, a second oil suction filter is provided between the walking variable pump and the liquid replenishing tank; the liquid replenishing tank is connected to the walking motor, and a second cooler and a second oil return filter are sequentially arranged between the walking motor and the liquid replenishing tank.

[0013] Preferably, the output pressure of the auxiliary gear pump is 20 MPa; the shift cylinder is a double-acting cylinder, and the pressure range is 1.5 - 3.0 MPa; the clutch cylinder is a normally open single-acting cylinder, and the pressure is 20 MPa.

[0014] Preferably, the auxiliary gear pump is connected to the shift cylinder and the clutch cylinder through a flow dividing valve; a first three-position four-way valve is arranged between the flow dividing valve and the shift cylinder, and a second three-position four-way valve is arranged between the flow dividing valve and the clutch cylinder; an unloading valve is arranged between the clutch cylinder and the second three-position four-way valve, and the unloading valve is connected to the fuel tank.

[0015] Preferably, a third oil suction filter is connected between the auxiliary gear pump and the fuel tank; the two three-position four-way valves are connected to the fuel tank through a third cooler.

[0016] Preferably, the auxiliary gear pump, the working gear pump, and the travel variable pump are provided with mechanical power through two independent PTO ports of the engine.

[0017] Compared with the prior art, the advantages and positive effects of the present utility model are as follows:

[0018] The present utility model provides power support for the control part hydraulic system, the hydraulic travel part, and the auxiliary control hydraulic part through one engine. The auxiliary control hydraulic part realizes the high and low gear conversion function of the tiller drive mechanism and the clutch engagement and disengagement control function between the working components and the engine flywheel end by controlling two three-position four-way valves; the control part hydraulic system controls the actions of the tipping cylinder and the lifting cylinder respectively through two multi-way directional control valves, thereby controlling the tipping function and the vertical lifting function of the working components; the hydraulic travel part realizes stepless speed regulation through the control circuit; the operating system is simple, which reduces the workload of the operator and is not prone to operating errors. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The accompanying drawings forming a part of this specification are used to provide a further understanding of the present utility model. The schematic embodiments and descriptions thereof of the present utility model are used to explain the present utility model and do not constitute an improper limitation to the present utility model.

[0020] Figure 1 is a schematic diagram of the control part hydraulic system of the embodiment of the present utility model;

[0021] Figure 2 is a schematic diagram of the hydraulic travel part of the embodiment of the present utility model;

[0022] Figure 3 is a schematic diagram of the auxiliary control hydraulic part of the embodiment of the present utility model;

[0023] In the figure:

[0024] 1 - control part hydraulic system, 101 - working gear pump, 102 - first filter, 103 - priority valve, 104 - hydraulic steering gear, 105 - steering cylinder, 106 - first cooler, 107 - first suction filter, 108 - fuel tank, 109 - tipping hydraulic lock, 110 - lifting hydraulic lock, 111 - tipping multi-way directional control valve, 112 - lifting multi-way directional control valve, 113 - tipping cylinder, 114 - lifting cylinder, 2 - hydraulic travel part, 21 - travel variable pump, 22 - variable motor, 23 - second cooler, 24 - second return oil filter, 25 - second suction filter, 26 - fluid replenishing tank, 3 - auxiliary control hydraulic part, 31 - auxiliary gear pump, 32 - third suction filter, 33 - third cooler, 34 - second three-position four-way valve, 35 - unloading valve, 36 - clutch cylinder, 37 - flow dividing valve, 38 - first three-position four-way valve, 39 - shifting cylinder. Detailed implementation mode

[0025] It should be noted that the following detailed description is illustrative and aims to provide further explanation of the present utility model. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by those of ordinary skill in the technical field to which the present utility model belongs.

[0026] The following combines with the drawings to elaborate on the present utility model in detail. A hydraulic system for a subsoiler disclosed in this embodiment includes three parts: a control part hydraulic system 1, a hydraulic walking part 2, and an auxiliary control hydraulic part 3, and uses one engine to provide mechanical power.

[0027] Among them, the control part hydraulic system 1 is used to control the lifting and flipping functions of the working components as a whole and the steering function of the subsoiler, while the rotation of the working component spiral cutter is powered by the flywheel end of the engine, and a clutch is provided between the working component and the flywheel end of the engine; the hydraulic walking part 2 controls the forward and backward movement of the driving mechanism of the subsoiler; the auxiliary control hydraulic part 3 controls the high and low gear conversion of the driving mechanism of the subsoiler and the clutch engagement and disengagement functions of the working components.

[0028] As Figure 1 shown, the control part hydraulic system 1 adopts a low-pressure open hydraulic control system, including a working gear pump 101, and the working gear pump 101 is powered by the engine; the working gear pump 101 is respectively connected to a steering cylinder 105, a flipping cylinder 113, and a lifting cylinder 114. The steering cylinder 105 controls the steering of the subsoiler, the flipping cylinder 113 controls the up and down flipping movement of the working components of the subsoiler, and the lifting cylinder 114 controls the up and down vertical movement of the working components of the subsoiler; hydraulic oil is delivered to the steering cylinder 105, the flipping cylinder 113, and the lifting cylinder 114 through the working gear pump 101.

[0029] As Figure 1 shown, the oil inlet of the working gear pump 101 is connected to the fuel tank 108 through an oil inlet pipeline, and a first oil suction filter 107 is provided between the working gear pump 101 and the fuel tank 108 to filter the hydraulic oil; the oil outlet of the working gear pump 101 is connected to the P port of a priority valve 103, and a first filter 102 is connected between the working gear pump 101 and the priority valve 103 to further filter the hydraulic oil about to enter each cylinder.

[0030] As Figure 1As shown, the CF port of the priority valve 103 is connected to the hydraulic steering gear 104, and the hydraulic steering gear 104 is connected to a steering cylinder 105; the EF port of the priority valve 103 is respectively connected to the P port of the tipping multi-way directional control valve 111 and the P port of the lifting multi-way directional control valve 112; the tipping multi-way directional control valve 111 is connected to a tipping hydraulic lock 109, and the tipping hydraulic lock 109 is connected to a tipping cylinder 113, the lifting multi-way directional control valve 112 is connected to a lifting hydraulic lock 110, and the lifting hydraulic lock 110 is connected to a lifting cylinder 114.

[0031] When the deep tillage machine is working in a straight line forward, the EF port of the priority valve 103 is opened and the CF port is closed, and the working gear pump 101 delivers oil to the tipping multi-way directional control valve 111 and the lifting multi-way directional control valve 112; the tipping cylinder 113 is controlled by the tipping multi-way directional control valve 111 to move back and forth, realizing different tipping actions of the working components of the deep tillage machine; the lifting cylinder 114 is controlled by the lifting multi-way directional control valve 112 to move back and forth, realizing different vertical lifting actions of the working components of the deep tillage machine. When tipping to the required position or lifting to the required position, the circuit of the tipping cylinder 113 or the lifting cylinder 114 is locked by controlling the tipping hydraulic lock 109 or the lifting hydraulic lock 110 at this time, so that its action remains unchanged.

[0032] As Figure 1 shown, the T port of the priority valve 103 is connected to the oil return pipeline, the T port of the tipping multi-way directional control valve 111 is connected to the oil return pipeline, the T port of the lifting multi-way directional control valve 112 is connected to the oil return pipeline, and the oil return pipeline is provided with a first cooler 106 at the oil return port of the fuel tank 108 to prevent the temperature of the hydraulic oil entering the fuel tank from being too high.

[0033] When the deep tillage machine needs to turn, at this time the CF port of the priority valve 103 is opened and the EF port is closed, and the working gear pump 101 delivers oil to the hydraulic steering gear 104, and then reaches the steering cylinder 105, enabling the deep tillage machine to realize the steering function of the front wheels, and the priority valve 103 can ensure the priority realization of the steering function.

[0034] As Figure 2 shown, the hydraulic walking part 2 adopts a closed-loop hydraulic system, including a walking variable pump 21, the walking variable pump 21 is connected to a variable motor 22, the oil inlet of the walking variable pump 21 is connected to the oil outlet of a replenishing liquid tank 26, and a second oil suction filter 25 is arranged between the walking variable pump 21 and the replenishing liquid tank 26; the oil return port of the replenishing liquid tank 26 is connected to the oil return port of the variable motor 22, and a second cooler 23 and a second oil return filter 24 are arranged in sequence between the variable motor 22 and the replenishing liquid tank 26.

[0035] The walking variable pump 21 provides mechanical energy through the deep tillage machine engine. The variable motor 22 is connected to the drive mechanism of the deep tillage machine. Further, the variable motor 22 is connected to the transmission of the drive mechanism of the deep tillage machine. It can be understood that the drive mechanism also includes a transmission mechanism, front and rear axles, front and rear wheels, etc. The transmission mechanism connects the transmission to the front and rear axles, so that the transmission can distribute power to the front and rear axles. When the walking variable pump 21 works, it can drive the variable motor 22 to rotate, and the variable motor 22 drives the drive mechanism to operate, finally realizing the walking drive function of the screw deep tillage machine. The hydraulic walking part can also achieve stepless speed regulation through the control circuit.

[0036] As Figure 3 shown, the auxiliary control hydraulic part 3 also adopts a low-pressure open hydraulic control system, including an auxiliary gear pump 31, and the output pressure of the auxiliary gear pump 31 is 20 MPa; the auxiliary gear pump 31 is connected to a shift cylinder 39 and a clutch cylinder 36. The shift cylinder 39 is a double-acting cylinder, and the pressure range is 1.5 - 3.0 MPa, which is used to control the high and low gear switching of the drive mechanism of the deep tillage machine. It can be understood that the shift cylinder 39 is used in matching with the transmission of the drive mechanism of the deep tillage machine, and can adjust the transmission by regulating the oil inlet of the shift cylinder 39, so as to realize the high and low gear switching of the drive mechanism of the deep tillage machine; the clutch cylinder 36 is a normally open single-acting cylinder, with a pressure of 20 MPa, which controls the clutch engagement and disengagement function between the working component and the engine flywheel.

[0037] As Figure 3 shown, in order to meet the low-pressure requirement of the shift cylinder 39, the oil outlet of the auxiliary gear pump 31 is connected to the shift cylinder 39 and the clutch cylinder 36 through a flow dividing valve 37; as Figure 3 shown, the oil inlet of the auxiliary gear pump 31 is connected to the oil outlet of the fuel tank 108, and a third oil suction filter 32 is connected between the auxiliary gear pump 31 and the fuel tank 108.

[0038] As Figure 3 shown, a first three-position four-way valve 38 is arranged between the flow dividing valve 37 and the shift cylinder 39, and a second three-position four-way valve 34 is arranged between the flow dividing valve 37 and the clutch cylinder 36. The flow dividing valve 37 is respectively connected to the P ports of the two three-position four-way valves. The T ports of the two three-position four-way valves are connected to the fuel tank 108 through a return oil pipeline, and a third cooler 33 is arranged at the return oil port of the fuel tank 108.

[0039] As Figure 3As shown in the figure, the first three-position four-way valve 38 is connected to the shift cylinder 39 through ports A1 and B1. Under the action of the first three-position four-way valve 38, by controlling the direction of the incoming oil, the shift cylinder 39 is made to perform different actions, thereby realizing the high and low gear switching of the driving mechanism of the subsoiler and controlling the traveling speed of the subsoiler during operation. The action of the clutch cylinder 36 is controlled by the second three-position four-way valve 34 to control the clutch between the working component and the engine flywheel end, thereby controlling the mechanical power of the working component. An unloading valve 35 is provided between the clutch cylinder 36 and the second three-position four-way valve 34 to relieve the pressure of the clutch cylinder in the state of shutting down the engine.

[0040] It can be understood that the auxiliary gear pump, the working gear pump, and the traveling variable pump provide mechanical power through two independent PTO ports of the engine, and two of the pumps are connected in parallel to one PTO.

[0041] The utility model only needs to control two three-position four-way valves to realize the high and low gear conversion function of the driving mechanism of the subsoiler and the clutch engagement and disengagement control function between the working component and the engine; the tipping function and the vertical lifting function of the hydraulic system of the control part of the subsoiler are respectively controlled by two multi-way directional control valves, and the operating system is simple, which reduces the work burden of the operator and is not prone to operating errors.

[0042] Although the specific implementation manners of the present utility model are described above in conjunction with the drawings, it is not a limitation on the protection scope of the present utility model. Those skilled in the art should understand that based on the technical solutions of the present utility model, various modifications or deformations that can be made by those skilled in the art without creative efforts are still within the protection scope of the present utility model.

Claims

1. A hydraulic system for a deep tiller, characterized in that: It includes a control part hydraulic system, a hydraulic travel part, and an auxiliary control hydraulic part, and uses an engine to provide mechanical power; the control part hydraulic system includes a working gear pump, one end of the working gear pump is connected to the oil tank, and the other end is connected to the P port of the priority valve, the CF port of the priority valve is connected to the steering cylinder, and the EF port of the priority valve is respectively connected to the flip multi-way reversing valve and the lifting multi-way reversing valve, the flip multi-way reversing valve is connected to the flip cylinder, and the lifting multi-way reversing valve is connected to the lifting cylinder; the travel part includes a travel variable pump, one end of the travel variable pump is connected to the liquid replenishing tank, and the other end is connected to the variable motor, and the variable motor is connected to the gearbox of the drive mechanism; the auxiliary control hydraulic part includes an auxiliary gear pump, the auxiliary gear pump is connected to the shift cylinder and the clutch cylinder, and the clutch cylinder controls the clutch between the flywheel end of the engine and the working component; The shift cylinder controls the gearbox of the drive mechanism.

2. A deep tiller hydraulic system as claimed in claim 1, characterized in that: A first oil suction filter is arranged between the working gear pump and the oil tank; and the first filter is connected between the working gear pump and the priority valve.

3. A deep tiller hydraulic system as claimed in claim 1, characterized in that: A turning hydraulic lock is connected between the turning multi-way reversing valve and the turning oil cylinder; a lifting hydraulic lock is connected between the lifting multi-way reversing valve and the lifting oil cylinder.

4. A deep tiller hydraulic system as claimed in claim 1, characterized in that: The T ports of the flip multi-way reversing valve, the lifting multi-way reversing valve and the priority valve are connected to the oil tank through the first cooler.

5. A deep tiller hydraulic system as claimed in claim 1, characterized in that: A hydraulic steering gear is connected between the CF port of the priority valve and the steering cylinder.

6. A deep tiller hydraulic system as claimed in claim 1, characterized in that: A second oil suction filter is arranged between the travel variable displacement pump and the liquid replenishing tank; the liquid replenishing tank is connected to the travel motor, and a second cooler and a second oil return filter are arranged in sequence between the travel motor and the liquid replenishing tank.

7. A deep tiller hydraulic system as claimed in claim 1, characterized in that: The output pressure of the auxiliary gear pump is 20MPa; the shift cylinder is a double-acting cylinder with a pressure range of 1.5-3.0MPa; the clutch cylinder is a normally open single-acting cylinder with a pressure of 20MPa.

8. The hydraulic system for a deep tiller according to claim 1, characterized in that: The auxiliary gear pump is connected to the shift cylinder and the clutch cylinder through a diverter valve; a first three-position four-way valve is arranged between the diverter valve and the shift cylinder, and a second three-position four-way valve is arranged between the diverter valve and the clutch cylinder; an unloading valve is arranged between the clutch cylinder and the second three-position four-way valve, and the unloading valve is connected to the oil tank.

9. A deep tiller hydraulic system as claimed in claim 8, characterized in that: A third oil suction filter is connected between the auxiliary gear pump and the oil tank; and the two three-position four-way valves are connected to the oil tank through a third cooler.

10. The hydraulic system for a deep tiller according to claim 1, characterized in that: The auxiliary gear pump, the working gear pump and the travel variable displacement pump provide mechanical power through two independent PTO ports of the engine.

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