Header composite profiling hydraulic system and agricultural harvesting machine adopting header composite profiling hydraulic system

Abstract

The utility model discloses a header composite profiling hydraulic system and an agricultural harvesting machine adopting the header composite profiling hydraulic system. Transverse active profiling control over the header can be achieved by controlling the reversing action of the first electromagnetic reversing valve, longitudinal active profiling control over the header can be achieved by controlling the reversing action of the second electromagnetic reversing valve and the reversing action of the third electromagnetic reversing valve, and therefore active composite profiling hydraulic control over the header can be achieved. Compared with existing mechanical passive profiling control, the profiling control precision is improved, the profiling flexibility and stability are improved, environment changes can be quickly responded, and corresponding adjustment can be made.

Description

Technical Field

[0001] The utility model relates to the technical field of cutter bar profiling, and in particular to a cutter bar composite profiling hydraulic system. In addition, the utility model also particularly relates to an agricultural harvesting machine adopting the above hydraulic system. Background Art

[0002] In recent years, with the continuous development of agricultural mechanization, cutter bar profiling technology has been gradually applied to some advanced combine harvesters and silage harvesters. The cutter bar profiling technology can realize the automatic adjustment of the cutter bar height, thereby improving the operation efficiency and profiling stability. However, the existing cutter bar profiling technology has the problem of poor profiling stability. For example, patent CN211881120U discloses a cutter bar profiling device for a silage harvester. The device realizes the lateral rotation and reset of the cutter bar through the mutual cooperation of components such as a swing frame, a cutter bar main frame and a return mechanism. Although the profiling ability of the cutter bar is improved to a certain extent, there is still the problem of poor profiling stability. Especially when facing sudden terrains, the stability of the cutter bar is difficult to guarantee. Summary of the Utility Model

[0003] The utility model provides a cutter bar composite profiling hydraulic system and an agricultural harvesting machine adopting the same, which can realize the active composite profiling hydraulic control of the cutter bar. Compared with the existing mechanical passive profiling control, not only the profiling control accuracy is improved, but also the profiling flexibility and stability are improved, and the system can quickly respond to environmental changes and make corresponding adjustments.

[0004] According to one aspect of the utility model, a cutter bar composite profiling hydraulic system is provided, which includes a hydraulic pump, a hydraulic oil tank, a first electromagnetic directional control valve, a double-acting cylinder, a second electromagnetic directional control valve, a third electromagnetic directional control valve, a first check valve, a first lifting cylinder and a second lifting cylinder. The inlet of the hydraulic pump is connected to the hydraulic oil tank, and the outlet is respectively connected to the first electromagnetic directional control valve, the second electromagnetic directional control valve and the third electromagnetic directional control valve. The first electromagnetic directional control valve is connected to the first oil port and the second oil port of the double-acting cylinder. The double-acting cylinder is used to drive the cutter bar for lateral adjustment, and the lateral active profiling control of the cutter bar is realized by controlling the commutation action of the first electromagnetic directional control valve. The second electromagnetic directional control valve is connected to the inlet of the first check valve. The outlet of the first check valve is connected to the rodless chambers of the first lifting cylinder and the second lifting cylinder. The first lifting cylinder and the second lifting cylinder are used to drive the cutter bar for longitudinal adjustment. The inlet of the third electromagnetic directional control valve is connected to the rodless chambers of the first lifting cylinder and the second lifting cylinder. The rod chambers of the first lifting cylinder and the second lifting cylinder, the first electromagnetic directional control valve and the third electromagnetic directional control valve are all connected to the hydraulic oil tank. The longitudinal active profiling control of the cutter bar is realized by controlling the commutation actions of the second electromagnetic directional control valve and the third electromagnetic directional control valve.

[0005] Further, a two-way balance valve is also provided between the first electromagnetic directional control valve and the double-acting oil cylinder.

[0006] Further, it also includes a second one-way valve, an electro-hydraulic proportional pressure reducing and overflow valve, and a fourth electromagnetic directional control valve. The oil inlet of the second one-way valve is connected to the oil outlet of the hydraulic pump. The oil outlet of the second one-way valve is connected to the oil inlet of the electro-hydraulic proportional pressure reducing and overflow valve. The oil outlet of the electro-hydraulic proportional pressure reducing and overflow valve is connected to the fourth electromagnetic directional control valve. The fourth electromagnetic directional control valve is also connected to the rodless chambers of the first lifting oil cylinder and the second lifting oil cylinder. By controlling the second electromagnetic directional control valve and the third electromagnetic directional control valve to lose power and the fourth electromagnetic directional control valve to be powered on, the longitudinal passive profiling of the cutting table can be achieved.

[0007] Further, it also includes a fifth electromagnetic directional control valve and a first accumulator. The fifth electromagnetic directional control valve is respectively connected to the rodless chambers of the first lifting oil cylinder and the second lifting oil cylinder, and the first accumulator.

[0008] Further, it also includes a sixth electromagnetic directional control valve and a second accumulator. The sixth electromagnetic directional control valve is respectively connected to the rodless chambers of the first lifting oil cylinder and the second lifting oil cylinder, and the second accumulator. The energy storage pressure of the second accumulator is higher than that of the first accumulator.

[0009] Further, it also includes a two-way overflow valve. The two ends of the two-way overflow valve are respectively connected to the two oil ports of the double-acting oil cylinder.

[0010] Further, the double-acting oil cylinder includes a first piston rod, a second piston rod, a cylinder barrel, end covers, a first spring, a second spring, a connecting cylinder body, a sealing assembly, and a piston sealing assembly. The first end of the connecting cylinder body is connected to the cutting table, and the second end is connected to the cylinder barrel. The first end of the first piston rod is located inside the cylinder barrel, and the second end extends outside the cylinder barrel and is connected to the cutting table. The first end of the second piston rod extends out of the cylinder barrel and then extends into the connecting cylinder body, and the second end is located inside the cylinder barrel. The first end of the first piston rod is fixedly connected to the second piston rod. The second piston rod is designed with a piston. There is an oil port on each side of the piston on the cylinder barrel. The piston sealing assembly is installed at the piston. The end covers are respectively arranged at both ends of the cylinder barrel. The first spring is sleeved on the first piston rod. The second spring is sleeved on the second piston rod. Both ends of the first spring and the second spring respectively abut against the end cover and the piston. The sealing assembly is installed at the end cover and is arranged close to the inside of the cylinder barrel.

[0011] Further, it also includes a seventh electromagnetic directional control valve and a throttling element. The first oil port of the seventh electromagnetic directional control valve is connected to the first oil port of the double-acting oil cylinder, the second oil port is connected to the first end of the throttling element, and the second end of the throttling element is connected to the second oil port of the double-acting oil cylinder.

[0012] Further, the first electromagnetic directional control valve includes a first two-position three-way proportional electromagnetic directional control valve and a second two-position three-way proportional electromagnetic directional control valve. The oil inlets of the first two-position three-way proportional electromagnetic directional control valve and the second two-position three-way proportional electromagnetic directional control valve are both connected to the oil outlet of the hydraulic pump. The oil outlets of the first two-position three-way proportional electromagnetic directional control valve and the second two-position three-way proportional electromagnetic directional control valve are respectively connected to the first oil port and the second oil port of the double-acting cylinder. The oil return ports of the first two-position three-way proportional electromagnetic directional control valve and the second two-position three-way proportional electromagnetic directional control valve are both connected to the hydraulic oil tank.

[0013] In addition, the present utility model also provides an agricultural harvesting machine, which adopts the cutting table composite profiling hydraulic system as described above.

[0014] The present utility model has the following beneficial effects:

[0015] For the cutting table composite profiling hydraulic system of the present utility model, the lateral active profiling control of the cutting table can be realized by controlling the commutation action of the first electromagnetic directional control valve, and the longitudinal active profiling control of the cutting table can be realized by controlling the commutation actions of the second electromagnetic directional control valve and the third electromagnetic directional control valve. Thus, the active composite profiling hydraulic control of the cutting table can be achieved. Compared with the existing mechanical passive profiling control, not only the profiling control accuracy is improved, but also the flexibility and stability of profiling are enhanced, and it can quickly respond to environmental changes and make corresponding adjustments.

[0016] In addition, the agricultural harvesting machine of the present utility model also has the above advantages.

[0017] In addition to the purposes, features and advantages described above, the present utility model has other purposes, features and advantages. The following will refer to the drawings to further elaborate on the present utility model in detail. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The drawings forming a part of this application are used to provide a further understanding of the present utility model. The schematic embodiments of the present utility model and their descriptions are used to explain the present utility model and do not constitute an improper limitation to the present utility model. In the drawings:

[0019] Figure 1 is a hydraulic principle schematic diagram of the cutting table composite profiling hydraulic system of the preferred embodiment of this application.

[0020] Figure 2 is a structural schematic diagram of the double-acting cylinder of the preferred embodiment of this application.

[0021] Figure 3 is a structural schematic diagram of the double-acting cylinder when it is in the left extreme position of the preferred embodiment of this application.

[0022] Figure 4It is a schematic structural diagram of the double-acting oil cylinder in the right extreme position of the preferred embodiment of the present application.

[0023] Figure 5 It is a schematic structural diagram of the double-acting oil cylinder of the preferred embodiment of the present application installed on the cutting table.

[0024] Explanation of reference numerals

[0025] 1. Hydraulic pump; 2. Hydraulic oil tank; 3. First electromagnetic directional valve; 4. Double-acting oil cylinder; 5. Second electromagnetic directional valve; 6. Third electromagnetic directional valve; 7. First check valve; 8. First lifting oil cylinder; 9. Second lifting oil cylinder; 10. Two-way balance valve; 11. Second check valve; 12. Electro-hydraulic proportional pressure reducing and overflow valve; 13. Fourth electromagnetic directional valve; 14. Fifth electromagnetic directional valve; 15. First accumulator; 16. Sixth electromagnetic directional valve; 17. Second accumulator; 18. Two-way overflow valve; 19. Seventh electromagnetic directional valve; 20. Throttle element; 21. Overflow valve; 31. First two-position three-way proportional electromagnetic directional valve; 32. Second two-position three-way proportional electromagnetic directional valve; 41. First piston rod; 42. Second piston rod; 43. Cylinder barrel; 44. End cover; 45. First spring; 46. Second spring; 47. Connecting cylinder block; 48. Sealing assembly; 49. Piston seal assembly; 410. Fastening screw. Detailed implementation manners

[0026] It should be noted that, without conflict, the embodiments in the present application and the features in the embodiments may be combined with each other. The present application will be described in detail below with reference to the drawings and in combination with the embodiments.

[0027] Refer to Figure 1As shown in the figure, a preferred embodiment of the present application provides a header compound profiling hydraulic system, including a hydraulic pump 1, a hydraulic oil tank 2, a first electromagnetic directional control valve 3, a double-acting cylinder 4, a second electromagnetic directional control valve 5, a third electromagnetic directional control valve 6, a first check valve 7, a first lifting cylinder 8 and a second lifting cylinder 9. The inlet of the hydraulic pump 1 is connected to the hydraulic oil tank 2, and the outlets are respectively connected to the first electromagnetic directional control valve 3, the second electromagnetic directional control valve 5 and the third electromagnetic directional control valve 6. The hydraulic pump 1 is used to provide high-pressure hydraulic oil for each hydraulic actuator. The first electromagnetic directional control valve 3 is connected to the first oil port and the second oil port of the double-acting cylinder 4, and the double-acting cylinder 4 is used to drive the header for lateral adjustment, and the lateral active profiling control of the header is realized by controlling the commutation action of the first electromagnetic directional control valve 3. For example, when the first electromagnetic directional control valve 3 is controlled to switch to the left side, the hydraulic oil enters the double-acting cylinder 4 from the first oil port L of the double-acting cylinder 4, pushing the piston rod of the double-acting cylinder 4 to move to the right, causing the header to tilt to the right side, and the return oil is output from the second oil port R of the double-acting cylinder 4 and flows to the hydraulic oil tank 2 through the first electromagnetic directional control valve 3; when the first electromagnetic directional control valve 3 is controlled to switch to the right side, the hydraulic oil enters the double-acting cylinder 4 from the second oil port R of the double-acting cylinder 4, pushing the piston rod of the double-acting cylinder 4 to move to the left, and the return oil is output from the first oil port L of the double-acting cylinder 4 and flows to the hydraulic oil tank 2 through the first electromagnetic directional control valve 3, causing the header to tilt to the left side. The second electromagnetic directional control valve 5 is connected to the inlet of the first check valve 7, the outlet of the first check valve 7 is connected to the rodless chambers of the first lifting cylinder 8 and the second lifting cylinder 9. The first lifting cylinder 8 and the second lifting cylinder 9 are used to drive the header for longitudinal adjustment. The inlet of the third electromagnetic directional control valve 6 is connected to the rodless chambers of the first lifting cylinder 8 and the second lifting cylinder 9. The rod chambers of the first lifting cylinder 8 and the second lifting cylinder 9, the first electromagnetic directional control valve 3 and the third electromagnetic directional control valve 6 are all connected to the hydraulic oil tank 2. The longitudinal active profiling control of the header is realized by controlling the commutation actions of the second electromagnetic directional control valve 5 and the third electromagnetic directional control valve 6. For example, when the second electromagnetic directional control valve 5 is controlled to switch to the oil path conduction and the third electromagnetic directional control valve 6 is controlled to switch to the oil path non-conduction, the hydraulic oil enters the rodless chambers of the first lifting cylinder 8 and the second lifting cylinder 9 through the second electromagnetic directional control valve 5 and the first check valve 7, thereby pushing the header to rise, and the oil in the rod chambers of the first lifting cylinder 8 and the second lifting cylinder 9 is directly output to the hydraulic oil tank 2; when the second electromagnetic directional control valve 5 is controlled to switch to the oil path non-conduction and the third electromagnetic directional control valve 6 is controlled to switch to the oil path conduction, under the action of the self-weight of the header, the first lifting cylinder 8 and the second lifting cylinder 9 are compressed, and the oil in the rodless chambers of the first lifting cylinder 8 and the second lifting cylinder 9 is output to the hydraulic oil tank 2 through the third electromagnetic directional control valve 6, thereby realizing the lowering action of the header.

[0028] It can be understood that for the header compound profiling hydraulic system of this embodiment, the lateral active profiling control of the header can be achieved by controlling the commutation action of the first electromagnetic directional valve 3, and the longitudinal active profiling control of the header can be achieved by controlling the commutation actions of the second electromagnetic directional valve 5 and the third electromagnetic directional valve 6. Thus, the active compound profiling hydraulic control of the header can be realized. Compared with the existing mechanical passive profiling control, it not only improves the profiling control accuracy, but also improves the flexibility and stability of profiling, and can quickly respond to environmental changes and make corresponding adjustments.

[0029] Among them, the second electromagnetic directional valve 5 and the third electromagnetic directional valve 6 are both preferably two-position two-way proportional electromagnetic directional valves. In addition, the first electromagnetic directional valve 3 includes a first two-position three-way proportional electromagnetic directional valve 31 and a second two-position three-way proportional electromagnetic directional valve 32. The oil inlets of the first two-position three-way proportional electromagnetic directional valve 31 and the second two-position three-way proportional electromagnetic directional valve 32 are both connected to the oil outlet of the hydraulic pump 1. The oil outlets of the first two-position three-way proportional electromagnetic directional valve 31 and the second two-position three-way proportional electromagnetic directional valve 32 are respectively connected to the first oil port and the second oil port of the double-acting cylinder 4. The oil return ports of the first two-position three-way proportional electromagnetic directional valve 31 and the second two-position three-way proportional electromagnetic directional valve 32 are both connected to the hydraulic oil tank 2. Of course, in other embodiments, the first electromagnetic directional valve 3 can also adopt a three-position four-way proportional electromagnetic directional valve with a neutral function of H type. It can be understood that by precisely controlling the energization value of the electromagnet, the continuous adjustment of the oil flow rate can be realized, thereby achieving the precise control of the tilt angle of the header, which not only improves the operation accuracy and stability of the header, but also makes the operation more convenient and intelligent. In addition, the header compound profiling hydraulic system further includes an overflow valve 21. One end of the overflow valve 21 is connected to the oil outlet of the hydraulic pump 1, and the other end is connected to the hydraulic oil tank 2, which can play a role in limiting the pressure of the whole system.

[0030] Optionally, a two-way balance valve 10 is further arranged between the first electromagnetic directional valve 3 and the double-acting cylinder 4, which can play functions such as balancing the load and preventing the double-acting cylinder 4 from overspeed. At the same time, the two-way balance valve 10 also has the performance of a hydraulic lock and can lock the position of the double-acting cylinder 4 when needed to ensure the stability of the header. Among them, the V1 port and the V2 port of the two-way balance valve 10 are respectively connected to the 1 port of the first two-position three-way proportional electromagnetic directional valve 31 and the second two-position three-way proportional electromagnetic directional valve 32, and the C1 port and the C2 port of the two-way balance valve 10 are respectively connected to the two oil ports of the double-acting cylinder 4.

[0031] In addition, the header compound profiling hydraulic system further includes a second one-way valve 11, an electro-hydraulic proportional pressure reducing and overflow valve 12, and a fourth electromagnetic directional control valve 13. The inlet of the second one-way valve 11 is connected to the outlet of the hydraulic pump 1, the outlet of the second one-way valve 11 is connected to the inlet of the electro-hydraulic proportional pressure reducing and overflow valve 12, the outlet of the electro-hydraulic proportional pressure reducing and overflow valve 12 is connected to the fourth electromagnetic directional control valve 13, and the fourth electromagnetic directional control valve 13 is also connected to the rodless chambers of the first lifting cylinder 8 and the second lifting cylinder 9. Controlling the second electromagnetic directional control valve 5 and the third electromagnetic directional control valve 6 to lose power and the fourth electromagnetic directional control valve 13 to be powered on can achieve the longitudinal passive profiling of the header.

[0032] In addition, the header compound profiling hydraulic system further includes a fifth electromagnetic directional control valve 14 and a first accumulator 15. The fifth electromagnetic directional control valve 14 is respectively connected to the rodless chambers of the first lifting cylinder 8 and the second lifting cylinder 9 and the first accumulator 15. Optionally, the header compound profiling hydraulic system further includes a sixth electromagnetic directional control valve 16 and a second accumulator 17. The sixth electromagnetic directional control valve 16 is respectively connected to the rodless chambers of the first lifting cylinder 8 and the second lifting cylinder 9 and the second accumulator 17, and the energy storage pressure of the second accumulator 17 is higher than that of the first accumulator 15. It can be understood that during the transfer operation, the type and weight of the header will directly affect the requirements and performance of the hydraulic system. When a light header is attached, the system can select the accumulator circuit with a lower pressure, that is, the first accumulator 15, to meet its basic hydraulic requirements. When a heavy header is attached, the system can select the accumulator circuit with a higher pressure, that is, the second accumulator 17. This design not only improves the adaptability of the hydraulic system to the header, but also enables the system to make dynamic adjustments according to the operation requirements to ensure that the header avoids large oscillations during the transfer operation, effectively control the amplitude and impact of the header, thereby protecting the header from damage and achieving the best operation effect.

[0033] Optionally, the header compound profiling hydraulic system further includes a bi-directional overflow valve 18. Both ends of the bi-directional overflow valve 18 are respectively connected to the two oil ports of the double-acting cylinder 4.

[0034] Optionally, the header compound profiling hydraulic system further includes a seventh electromagnetic directional control valve 19 and a throttling element 20. The first oil port of the seventh electromagnetic directional control valve 19 is connected to the first oil port of the double-acting cylinder 4, the second oil port is connected to the first end of the throttling element 20, and the second end of the throttling element 20 is connected to the second oil port of the double-acting cylinder 4. Among them, the throttling element 20 can be a adjustable throttle valve or a damper. When controlling the seventh electromagnetic directional control valve 19 to switch to the oil path conduction, the left oil chamber and the right oil chamber of the double-acting cylinder 4 are connected, and at this time, the double-acting cylinder 4 is in a floating state, so that the header can automatically adjust its attitude when encountering an uneven ground or an obstacle, realizing the passive profiling of the header.

[0035] Among them, asFigures 2 to 5 As shown, the double-acting oil cylinder 4 includes a first piston rod 41, a second piston rod 42, a cylinder barrel 43, end caps 44, a first spring 45, a second spring 46, a connecting cylinder body 47, a sealing assembly 48 and a piston sealing assembly 49. The first end of the connecting cylinder body 47 is connected to the cutter bar, and the second end is connected to the cylinder barrel 43. Specifically, the second end of the connecting cylinder body 47 is fixedly connected to the cylinder barrel 43 by fastening screws 410. The first end of the first piston rod 41 is located inside the cylinder barrel 43, and the second end extends outside the cylinder barrel 43 and is connected to the cutter bar. The first end of the second piston rod 42 extends outside the cylinder barrel 43 and then extends into the connecting cylinder body 47, and the second end is located inside the cylinder barrel 43. The first end of the first piston rod 41 is fixedly connected to the second piston rod 42. The second piston rod 42 is designed with a piston. One oil port is respectively arranged on both sides of the piston on the cylinder barrel 43. The piston sealing assembly 49 is installed at the piston to prevent the oil fluid from flowing between the left oil chamber and the right oil chamber. The end caps 44 are respectively arranged at both ends of the cylinder barrel 43. Specifically, the end caps 44 are fixed at both ends of the cylinder barrel 43 by threaded connection. The first spring 45 is sleeved on the first piston rod 41, and the second spring 46 is sleeved on the second piston rod 42. Both ends of the first spring 45 and the second spring 46 respectively abut against the end caps 44 and the piston. The sealing assembly 48 is installed at the end caps 44 and is arranged close to the inside of the cylinder barrel 43 to prevent the oil fluid from leaking from both end caps 44. Among them, both the first piston rod 41 and the second piston rod 42 are designed with stepped shafts, which is beneficial to improving the stability and load-bearing capacity of the piston rods and can also effectively prevent the springs from being over-compressed. In addition, the second end of the first piston rod 41 is designed with a ball head structure, which not only ensures the flexible connection between components but also ensures the tightness of the connection, preventing performance degradation or failures caused by loosening. Among them, the first end of the first piston rod 41 is designed with an external thread, and the second end of the second piston rod 42 is designed with an internal thread, and the two are fixedly connected through threaded cooperation. In addition, the connecting cylinder body 47 is provided with a vent hole to ensure the normal extension and retraction of the piston rod.

[0036] It can be understood that the longitudinal active profiling process of the composite profiling hydraulic system of the cutting platform of the utility model is as follows: when the cutting platform needs to rise, the hydraulic pump 1 starts to output high-pressure oil, and at this time, the electromagnet c of the second electromagnetic reversing valve 5 is energized, so that the port 1 and the port 2 of the valve are connected, and the opening size of the conducting port is proportional to the power value of the electromagnet c, which ensures that the oil can enter the rodless chamber of the two lifting cylinders at a suitable flow rate and pressure. At the same time, the electromagnet d of the third electromagnetic reversing valve 6 is not energized, so its port 1 and the port 2 are not connected. In this way, the high-pressure oil can smoothly pass through the second electromagnetic reversing valve 5 and the first one-way valve 7 into the rodless chamber of the two lifting cylinders, thereby pushing the two lifting cylinders to rise synchronously and realize the rise of the cutting platform. When the cutting platform needs to be lowered, the electromagnet d of the third electromagnetic reversing valve 6 is energized, so that its port 1 is connected to port 2. At this time, the electromagnet c of the second electromagnetic reversing valve 5 is no longer energized, so its corresponding valve port is not connected, and the port 2 to port 1 of the first one-way valve 7 is also not connected. In this way, the lifting cylinder of the cutting platform will retract due to its own weight. During the retraction process, the oil in the rodless chamber of the lifting cylinder will pass through the third electromagnetic reversing valve 6 and flow into the hydraulic oil tank 2, thereby completing the lowering action of the cutting platform.

[0037] In addition, the longitudinal passive profiling process is as follows: the electromagnet c of the second electromagnetic reversing valve 5 loses power, the electromagnet d of the third electromagnetic reversing valve 6 loses power, the electromagnet g of the fourth electromagnetic reversing valve 13 is energized and opened, the hydraulic pump 1 pumps oil and enters the rodless chambers of the two lifting cylinders through the electric proportional pressure reducing relief valve 12. Under the weight of the cutting platform, the two lifting cylinders do not extend but provide a stable supporting force to the cutting platform, reducing the weight of the cutting platform on the ground. At the same time, the output current of the electric proportional pressure reducing relief valve 12 is adjusted to change the pressure of the two lifting cylinders, thereby adjusting the auxiliary supporting force of the two lifting cylinders to the cutting platform, so that the cutting platform can achieve the best profiling effect under various terrains. During the harvesting process of the harvesting platform, the harvesting platform is pushed up and down according to the undulation of the ground. When encountering a raised ground, the harvesting platform moves upward, driving the two lifting cylinders to extend, and the oil pressure in the two lifting cylinders is reduced. The hydraulic pump 1 pumps the oil and replenishes it into the two lifting cylinders through the electric proportional pressure reducing relief valve 12, so that the pressure in the two lifting cylinders is stabilized at the set value; when encountering a pitted ground, the harvesting platform is compressed and the two lifting cylinders descend, and the oil pressure in the two lifting cylinders increases. A part of the oil in the two lifting cylinders overflows from the electric proportional pressure reducing relief valve 12 and flows back to the hydraulic oil tank 2, so that the pressure in the two lifting cylinders is stabilized at the set value, thereby achieving the purpose of passive profiling.

[0038] In addition, the lateral active profiling process is as follows: when the hydraulic pump 1 outputs high-pressure oil, the electromagnet a of the first two-position three-way proportional electromagnetic reversing valve 31 is energized, and at this time, its port 1 is connected to the port 3, and the opening size of the conducting port is proportional to the energization value of the electromagnet a, which allows the oil flow to be accurately controlled as needed. The high-pressure oil enters the left chamber of the double-acting oil cylinder 4 through the first two-position three-way proportional electromagnetic reversing valve 31, the two-way balancing valve 10 and the L port of the double-acting oil cylinder 4, pushing the piston rod to extend to the right, thereby causing the cutting platform to tilt to the right. At the same time, since the electromagnet b of the second two-position three-way proportional electromagnetic reversing valve 32 is not energized, its port 1 is connected to the port 2, and the oil in the right chamber of the double-acting oil cylinder 4 flows back to the hydraulic oil tank 2 through the two-way balancing valve 10 and the second two-position three-way proportional electromagnetic reversing valve 32. Among them, when the horizontal profiling of the cutting platform is at the right tilt limit, the piston rod of the double-acting oil cylinder 4 extends to the right to the right limit position. At this time, the stepped shoulder of the first piston rod 41 is in close contact with the end cover 44 on this side, which plays a role of limiting and effectively prevents the damage caused by excessive compression of the spring. When the cutting platform needs to tilt to the left, the hydraulic pump 1 continues to output high-pressure oil, but at this time, the electromagnet b of the second two-position three-way proportional electromagnetic reversing valve 32 is energized, so that its port 1 is connected to the port 3, and the high-pressure oil enters the right chamber of the double-acting oil cylinder 4 through the second two-position three-way proportional electromagnetic reversing valve 32, the two-way balancing valve 10 and the R port of the double-acting oil cylinder 4, pushing the piston rod to extend to the left, and the cutting platform tilts to the left. At this time, the electromagnet a of the first two-position three-way proportional electromagnetic reversing valve 31 is not energized, and its port 1 is connected to the port 2. The oil in the left chamber of the double-acting oil cylinder 4 flows back to the hydraulic oil tank 2 through the two-way balancing valve 10 and the first two-position three-way proportional electromagnetic reversing valve 31. Among them, when the lateral profiling of the cutting platform is at the left tilt limit, the piston rod of the double-acting oil cylinder 4 extends to the left to the left limit position, and the stepped shoulder of the second piston rod 42 is in close contact with the side end cover 44, which also plays a role of limiting and protecting. In the active lateral profiling process of the cutting platform, the two-way balance valve 10 plays a vital role. They can ensure that the double-acting oil cylinder 4 remains stable during the movement, effectively solving the stall and overspeed problems that may occur when the cutting platform swings left and right. At the same time, the two-way balance valve 10 also has the performance of a hydraulic lock, which can lock the oil cylinder position when necessary to ensure the stability of the cutting platform. In addition, the two-way relief valve 18 can effectively protect the cutting platform and the hydraulic system during the lateral profiling of the cutting platform. When the cutting platform is in the lateral tilt limit position, the two-way relief valve 18 begins to overflow and unload, so that a certain pressure is maintained in the oil chamber of the double-acting oil cylinder 4 to avoid pressure shock, thereby protecting the cutting platform from damage.

[0039] In addition, the lateral passive profiling process is as follows: in the passive profiling mode, the lateral profiling of the cutter bar mainly depends on the first spring 45 and the second spring 46 built in the double-acting cylinder 4. When the left side of the cutter bar encounters a protrusion or a raised ground surface, the cutter bar will tilt to the right, and the double-acting cylinder 4 will extend to the right. At this time, the first spring 45 in the right oil chamber is compressed, and the second spring 46 in the left oil chamber is also in a compressed state. After the cutter bar passes over the protrusion, due to its own weight and the spring force of the first spring 45 being greater than that of the second spring 46, the cutter bar will gradually return to the horizontal position. Similarly, when the right side of the cutter bar encounters a protrusion, a similar tilting and restoring process will occur. In addition, the electromagnet e of the seventh electromagnetic directional valve 19 can be controlled to be energized, so that its port 1 is communicated with port 2, thereby connecting the left oil chamber and the right oil chamber of the double-acting cylinder 4. At this time, the cylinder is in a floating state. This floating state enables the cutter bar to automatically adjust its posture when encountering uneven ground or obstacles, maintaining a stable operating state. The throttling element 20 can effectively slow down the flow rate of the oil in the cylinder, thereby increasing the smoothness of the lateral profiling of the cutter bar and reducing the vibration and impact caused by uneven ground. In addition, when the cutter bar encounters a large impact or obstacle, if the oil in the double-acting cylinder 4 cannot be discharged in time through the throttling element 20, the two-way overflow valve 18 will automatically open to allow the oil to pass through quickly, thereby avoiding the damage to the hydraulic system caused by instantaneous high pressure.

[0040] In addition, when transferring or driving on a road surface, other solenoid valves are de-energized, and only the electromagnet h of the fifth electromagnetic directional valve 14 or the electromagnet i of the sixth electromagnetic directional valve 16 is energized. At this time, the first accumulator 15 or the second accumulator 17 is communicated with the rodless chambers of the two lifting cylinders. The accumulator can absorb the impact caused by the oscillation of the cutter bar, reduce the oscillation amplitude of the cutter bar, and effectively solve the oscillation problem of the cutter bar during transfer or high-speed driving.

[0041] In addition, another embodiment of the present utility model further provides an agricultural harvesting machine, preferably adopting the cutter bar composite profiling hydraulic system as described above. Among them, the agricultural harvesting machine can be a combine harvester, a silage harvester, a tomato harvester or other agricultural harvesting machines with a cutter bar.

[0042] The above are only the preferred embodiments of the present utility model and are not used to limit the present utility model. For those skilled in the art, the present utility model can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model shall be included within the protection scope of the present utility model.

Claims

1. A composite profiling hydraulic system for a cutting platform, characterized in that: The invention comprises a hydraulic pump (1), a hydraulic oil tank (2), a first electromagnetic reversing valve (3), a double-acting oil cylinder (4), a second electromagnetic reversing valve (5), a third electromagnetic reversing valve (6), a first non-return valve (7), a first lifting oil cylinder (8) and a second lifting oil cylinder (9); the oil inlet of the hydraulic pump (1) is connected to the hydraulic oil tank (2); the oil outlet is respectively connected to the first electromagnetic reversing valve (3), the second electromagnetic reversing valve (5) and the third electromagnetic reversing valve (6); the first electromagnetic reversing valve (3) is connected to the first oil port and the second oil port of the double-acting oil cylinder (4); the double-acting oil cylinder (4) is used to drive the cutting platform to perform lateral adjustment; the lateral active profiling control of the cutting platform is realized by controlling the reversing action of the first electromagnetic reversing valve (3); The second electromagnetic reversing valve (5) is connected to the oil inlet of the first non-return valve (7); the oil outlet of the first non-return valve (7) is connected to the rodless chambers of the first lifting cylinder (8) and the second lifting cylinder (9); the first lifting cylinder (8) and the second lifting cylinder (9) are used to drive the cutting platform to make longitudinal adjustments; the oil inlet of the third electromagnetic reversing valve (6) is connected to the rodless chambers of the first lifting cylinder (8) and the second lifting cylinder (9); the rod chambers of the first lifting cylinder (8) and the second lifting cylinder (9), the first electromagnetic reversing valve (3) and the third electromagnetic reversing valve (6) are all connected to the hydraulic oil tank (2); and the longitudinal active profiling control of the cutting platform is realized by controlling the reversing action of the second electromagnetic reversing valve (5) and the third electromagnetic reversing valve (6).

2. The composite profiling hydraulic system for a cutting platform according to claim 1, characterized in that: A two-way balancing valve (10) is also provided between the first electromagnetic reversing valve (3) and the double-acting oil cylinder (4).

3. The composite profiling hydraulic system for a cutting platform according to claim 1, characterized in that: The utility model also comprises a second one-way valve (11), an electric proportional pressure reducing relief valve (12) and a fourth electromagnetic reversing valve (13); the oil inlet of the second one-way valve (11) is connected to the oil outlet of the hydraulic pump (1); the oil outlet of the second one-way valve (11) is connected to the oil inlet of the electric proportional pressure reducing relief valve (12); the oil outlet of the electric proportional pressure reducing relief valve (12) is connected to the fourth electromagnetic reversing valve (13); the fourth electromagnetic reversing valve (13) is also connected to the rodless chambers of the first lifting cylinder (8) and the second lifting cylinder (9); the second electromagnetic reversing valve (5) and the third electromagnetic reversing valve (6) are both de-energized and the fourth electromagnetic reversing valve (13) is energized, so that the longitudinal passive profiling of the cutting platform can be realized.

4. The composite profiling hydraulic system for a cutting platform according to claim 1, characterized in that: It also includes a fifth electromagnetic reversing valve (14) and a first accumulator (15). The fifth electromagnetic reversing valve (14) is connected to the rodless chamber of the first lifting cylinder (8) and the second lifting cylinder (9) and the first accumulator (15) respectively.

5. The composite profiling hydraulic system for a header according to claim 4, characterized in that: It also includes a sixth electromagnetic reversing valve (16) and a second accumulator (17). The sixth electromagnetic reversing valve (16) is connected to the rodless chamber of the first lifting cylinder (8) and the second lifting cylinder (9) and the second accumulator (17) respectively. The storage pressure of the second accumulator (17) is higher than that of the first accumulator (15).

6. The composite profiling hydraulic system for a cutting platform according to claim 1, characterized in that: It also comprises a two-way overflow valve (18), the two ends of which are respectively connected to the two oil ports of the double-acting oil cylinder (4).

7. The composite profiling hydraulic system for a header according to claim 1, characterized in that: The double-acting oil cylinder (4) comprises a first piston rod (41), a second piston rod (42), a cylinder barrel (43), an end cover (44), a first spring (45), a second spring (46), a connecting cylinder body (47), a sealing assembly (48) and a piston sealing assembly (49). The first end of the connecting cylinder body (47) is connected to a cutting platform, and the second end is connected to the cylinder barrel (43). The first end of the first piston rod (41) is located in the cylinder barrel (43), and the second end extends out of the cylinder barrel (43) and is connected to the cutting platform. The first end of the second piston rod (42) extends out of the cylinder barrel (43) and then extends into the connecting cylinder body (47), and the second end is located in the cylinder barrel (43). The first piston rod ( The first end of the cylinder (43) is fixedly connected to the second piston rod (41), the second piston rod (42) is designed with a piston, an oil port is respectively arranged on both sides of the piston on the cylinder (43), the piston sealing assembly (49) is installed at the piston, the end covers (44) are respectively arranged at the two ends of the cylinder (43), the first spring (45) is sleeved on the first piston rod (41), the second spring (46) is sleeved on the second piston rod (42), the two ends of the first spring (45) and the second spring (46) are respectively abutted against the end cover (44) and the piston, and the sealing assembly (48) is installed at the end cover (44) and arranged close to the cylinder (43).

8. The composite profiling hydraulic system for a header according to claim 1, characterized in that: It also includes a seventh electromagnetic reversing valve (19) and a throttling element (20), wherein the first oil port of the seventh electromagnetic reversing valve (19) is connected to the first oil port of the double-acting oil cylinder (4), the second oil port is connected to the first end of the throttling element (20), and the second end of the throttling element (20) is connected to the second oil port of the double-acting oil cylinder (4).

9. The composite profiling hydraulic system for a header according to claim 1, characterized in that: The first electromagnetic reversing valve (3) comprises a first two-position three-way proportional electromagnetic reversing valve (31) and a second two-position three-way proportional electromagnetic reversing valve (32); the oil inlets of the first two-position three-way proportional electromagnetic reversing valve (31) and the second two-position three-way proportional electromagnetic reversing valve (32) are both connected to the oil outlet of the hydraulic pump (1); the oil outlets of the first two-position three-way proportional electromagnetic reversing valve (31) and the second two-position three-way proportional electromagnetic reversing valve (32) are respectively connected to the first oil outlet and the second oil outlet of the double-acting oil cylinder (4); and the oil return ports of the first two-position three-way proportional electromagnetic reversing valve (31) and the second two-position three-way proportional electromagnetic reversing valve (32) are both connected to the hydraulic oil tank (2).

10. An agricultural harvesting machine, characterized in that: A composite cutting platform profiling hydraulic system as described in any one of claims 1 to 9 is used.

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