Hydraulic System and Hydraulic Control Method of a Self-Propelled Mowing and Flattening Machine

Abstract

The present invention provides a hydraulic system and a hydraulic control method for a self-propelled mowing and rolling machine. The hydraulic system of the self-propelled mowing and rolling machine includes: an integrated hydraulic valve block, a cutter bar lifting oil cylinder, a cutter bar tilting oil cylinder, a plurality of roller gap adjustment oil cylinders, and a pair of floating oil cylinders. The cutter bar lifting oil cylinder, the cutter bar tilting oil cylinder, the plurality of roller gap adjustment oil cylinders, and the pair of floating oil cylinders are all connected to the integrated hydraulic valve block through pipelines. Multiple groups of hydraulic control valves are integrated in the integrated hydraulic valve block, and the integrated hydraulic valve block is used to control the cutter bar lifting oil cylinder, the cutter bar tilting oil cylinder, the plurality of roller gap adjustment oil cylinders, and the pair of floating oil cylinders to perform corresponding operations, which facilitates the operation of the hydraulic system, simplifies the pipeline structure, reduces the hydraulic pipelines, improves the integration degree, and is convenient for the installation and maintenance of the hydraulic valve block.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle hydraulic systems, and in particular to a hydraulic system and a hydraulic control method for a self-propelled mowing and flattening machine. Background Art

[0002] At present, with the development of agricultural mechanization, large self-propelled mowers have been more widely used. As an important hydraulic control part of the whole self-propelled mower, the convenience, flexibility, compoundability, reliability, etc. of its control directly affect the performance of the whole machine. The existing hydraulic system of self-propelled mowers is mainly controlled by on-off valves, with low integration, numerous and complex pipelines. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to provide a hydraulic system and a hydraulic control method for a self-propelled mowing and flattening machine in view of the deficiencies of the prior art.

[0004] The technical solution for the present invention to solve the above technical problem is as follows: A hydraulic system for a self-propelled mowing and flattening machine, which includes: an integrated hydraulic valve block, a cutting table lifting oil cylinder, a cutting table tilting oil cylinder, a plurality of flattening roller gap adjustment oil cylinders, and a pair of floating oil cylinders. The cutting table lifting oil cylinder, the cutting table tilting oil cylinder, the plurality of flattening roller gap adjustment oil cylinders, and the pair of floating oil cylinders are all connected to the integrated hydraulic valve block through pipelines.

[0005] The beneficial effect of the present invention is: By designing a hydraulic system for a self-propelled mowing and flattening machine with an integrated hydraulic valve block, a cutting table lifting oil cylinder, a cutting table tilting oil cylinder, a plurality of flattening roller gap adjustment oil cylinders, and a pair of floating oil cylinders, a plurality of hydraulic control valves are integrated in the integrated hydraulic valve block, and the integrated hydraulic valve block is used to control the cutting table lifting oil cylinder, the cutting table tilting oil cylinder, the plurality of flattening roller gap adjustment oil cylinders, and the pair of floating oil cylinders to perform corresponding operations, which is convenient for the operation of the hydraulic system, reduces the number of pump sources, improves the utilization rate of power components, avoids performance waste, and optimizes the overall machine cost. Simplify the pipeline structure, reduce hydraulic pipelines, improve the integration degree, and facilitate the installation and maintenance of the hydraulic valve block.

[0006] Further, the integrated hydraulic valve block includes: a header lifting mechanism, a header tilting mechanism, a flattening roller rolling pressure adjustment mechanism, a header automatic profiling mechanism, a first hydraulic oil inlet, a second hydraulic oil inlet, a first oil return port for connecting to a hydraulic oil tank, and a second oil return port for connecting to a hydraulic oil tank. The header lifting mechanism, the header tilting mechanism, the flattening roller rolling pressure adjustment mechanism, and the header automatic profiling mechanism are all connected to the first hydraulic oil inlet through pipelines. The header lifting mechanism is connected to the second hydraulic oil inlet through a pipeline. The header lifting mechanism, the header tilting mechanism, the flattening roller rolling pressure adjustment mechanism, and the header automatic profiling mechanism are all connected to the first oil return port through pipelines. The header lifting mechanism is connected to the second oil return port through a pipeline. The header lifting mechanism is connected to the header lifting oil cylinder through a pipeline. The header tilting mechanism is connected to the header tilting oil cylinder through a pipeline. The flattening roller rolling pressure adjustment mechanism is respectively connected to a plurality of flattening roller gap adjustment oil cylinders through pipelines. The header automatic profiling mechanism is respectively connected to a pair of floating oil cylinders through pipelines.

[0007] The beneficial effects of adopting the above further solution are as follows: The settings of the header lifting mechanism, the header tilting mechanism, the flattening roller rolling pressure adjustment mechanism, the header automatic profiling mechanism, the first hydraulic oil inlet, the second hydraulic oil inlet, the first oil return port, and the second oil return port facilitate the manufacture of the integrated hydraulic valve block. Multiple sets of hydraulic control valves are integrated into the integrated hydraulic valve block, and the integrated hydraulic valve block is used to control the header lifting oil cylinder, the header tilting oil cylinder, a plurality of flattening roller gap adjustment oil cylinders, and a pair of floating oil cylinders to perform corresponding operations, which facilitates the operation of the hydraulic system, reduces the number of pump sources, improves the utilization rate of power components, avoids performance waste, and optimizes the overall machine cost. The pipeline structure is simplified, the hydraulic pipelines are reduced, the integration degree is improved, and it is convenient for the installation and maintenance of the hydraulic valve block.

[0008] Further, the integrated hydraulic valve block further includes: a proportional pressure reducing valve, a braking solenoid valve, and a parking brake release port for connecting to a wheel side reducer brake. The flattening roller rolling pressure adjustment mechanism and the header automatic profiling mechanism are both connected to the first end of the proportional pressure reducing valve through pipelines. The second end of the proportional pressure reducing valve is connected to the first hydraulic oil inlet through a pipeline. The third end of the proportional pressure reducing valve is connected to the second oil return port through a pipeline. The first end of the braking solenoid valve is connected to the second hydraulic oil inlet through a pipeline. The second end of the braking solenoid valve is connected to the parking brake release port through a pipeline. The third end of the braking solenoid valve is connected to the second oil return port.

[0009] The beneficial effects of adopting the above further solution are as follows: A proportional pressure reducing valve is newly added in the integrated hydraulic valve block, enabling precise control of floating profiling and flattening roller gap adjustment, and enhancing the reliability of the whole machine. When it is necessary to release the parking brake, the brake solenoid valve is energized, and the hydraulic oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out from the parking brake release port and then enters the wheel side reducer brake to release the parking brake. When the whole machine shuts down, the brake solenoid valve loses power and automatically enters the parking brake state.

[0010] Further, the flattening roller pressing adjustment mechanism includes: a flattening roller accumulator charging solenoid valve, a flattening roller accumulator pressure relief solenoid valve, and a flattening roller pressing adjustment port for connecting with a plurality of the flattening roller gap adjustment cylinders. The first end of the flattening roller accumulator charging solenoid valve is connected to the first hydraulic oil inlet through a pipeline. The second end of the flattening roller accumulator charging solenoid valve is connected to one end of the flattening roller accumulator pressure relief solenoid valve through a pipeline. The other end of the flattening roller accumulator pressure relief solenoid valve is connected to a plurality of the flattening roller gap adjustment cylinders through the flattening roller pressing adjustment port. The third end of the flattening roller accumulator charging solenoid valve is connected to the first end of the proportional pressure reducing valve through a pipeline. A plurality of the flattening roller gap adjustment cylinders are all connected with a flattening roller pressing accumulator. The flattening roller pressing adjustment port is connected with a first pressure sensor, and the first pressure sensor is connected to the proportional pressure reducing valve.

[0011] The beneficial effects of adopting the above further solution are as follows: The pressurized flattening roller pressing accumulator is connected to four flattening roller gap adjustment cylinders, forming an independent hydraulic flattening system. This system is equipped with a pressure sensor for monitoring the system pressure. According to different harvested crops and their growth conditions, this hydraulic flattening system requires different pressures. When it is necessary to increase the flattening roller pressure, the flattening roller accumulator charging solenoid valve is energized. At this time, the outlet pressure of the proportional pressure reducing valve is changed by adjusting the control current or voltage of the proportional pressure reducing valve, that is, the pressure charged into the hydraulic flattening system. During the charging process, it is judged whether the target flattening roller pressure is reached through the pressure value fed back by the pressure sensor and dynamic correction is carried out. After reaching the required pressure value, the charging is completed. When it is necessary to reduce the flattening roller pressure, the flattening roller accumulator pressure relief solenoid valve is energized, and the high-pressure oil in the hydraulic flattening system flows back to the hydraulic oil tank from the first oil return port.

[0012] Further, a pair of floating oil cylinders are a left floating oil cylinder and a right floating oil cylinder. The header automatic profiling mechanism includes: a left floating accumulator charging solenoid valve, a right floating accumulator charging solenoid valve, a left floating accumulator pressure relief solenoid valve, a right floating accumulator pressure relief solenoid valve, a left header automatic profiling port for connecting with the left floating oil cylinder, and a right header automatic profiling port for connecting with the right floating oil cylinder. The first end of the left floating accumulator charging solenoid valve is connected to the first hydraulic oil inlet pipeline. The second end of the left floating accumulator charging solenoid valve is connected to one end of the left floating accumulator pressure relief solenoid valve through a pipeline. The other end of the left floating accumulator pressure relief solenoid valve is connected to the left floating oil cylinder through the left header automatic profiling port. The third end of the left floating accumulator charging solenoid valve is connected to the first end of the proportional pressure reducing valve through a pipeline. The first end of the right floating accumulator charging solenoid valve is connected to the first hydraulic oil inlet pipeline. The second end of the right floating accumulator charging solenoid valve is connected to one end of the right floating accumulator pressure relief solenoid valve through a pipeline. The other end of the right floating accumulator pressure relief solenoid valve is connected to the right floating oil cylinder through the right header automatic profiling port. The third end of the right floating accumulator charging solenoid valve is connected to the first end of the proportional pressure reducing valve through a pipeline. The left floating oil cylinder is connected with a left floating accumulator, and the right floating oil cylinder is connected with a right floating accumulator. Second pressure sensors are installed at both the left header automatic profiling port and the right header automatic profiling port, and the second pressure sensors are connected to the proportional pressure reducing valve.

[0013] The beneficial effects of adopting the above further solution are as follows: During the operation of the self-propelled mowing and rolling machine, it is necessary to float up and down according to the undulation of the ground. If the lifting and lowering functions of the cutter bar are used to control the up and down floating of the cutter bar, the driver needs to highly concentrate and repeatedly issue commands for lifting and lowering the cutter bar, which is cumbersome in operation. By connecting the left floating accumulator and the right floating accumulator to the large chambers of the left floating oil cylinder and the right floating oil cylinder, an automatic profiling hydraulic system can be formed to achieve the automatic profiling function of the cutter bar. In this system, the left floating oil cylinder and the right floating oil cylinder support both sides of the cutter bar through a mechanical structure, and the pressure in the left floating accumulator and the right floating accumulator balances the self-weight of the cutter bar, enabling the cutter bar to float on the ground. A pressure sensor is installed on both the left and right sides of this system to monitor the floating pressure on that side. According to different ground conditions, this system requires different floating pressures. Taking the adjustment of the left floating pressure as an example, when it is necessary to pressurize the left floating accumulator, the charging solenoid valve of the left floating accumulator is energized. At this time, the outlet pressure of the proportional pressure reducing valve is changed by adjusting the control current or voltage of the proportional pressure reducing valve, that is, the pressure charged into the automatic profiling hydraulic system. During the pressurization process, it is judged whether the target rolling pressure of the flattening roller is reached through the pressure value feedback by the pressure sensor and dynamic correction is carried out. After reaching the required pressure value, the pressurization is completed. When it is necessary to relieve the pressure of the left floating accumulator, the pressure relief solenoid valve of the left floating accumulator is energized, and the hydraulic oil in the left automatic profiling hydraulic system flows back to the hydraulic oil tank through the first oil return port. Similarly, the floating pressure of the right automatic profiling hydraulic system can be adjusted in the same way, and the floating pressures on the left and right sides can be adjusted separately.

[0014] Further, the cutter bar lifting mechanism includes: a cutter bar lifting solenoid valve, a cutter bar lowering solenoid valve, a cutter bar lowering port for connecting with the cutter bar lifting oil cylinder, and a cutter bar lifting port for connecting with the cutter bar lifting oil cylinder. The first end of the cutter bar lifting solenoid valve is connected to the first hydraulic oil inlet port through a pipeline. The second end of the cutter bar lifting solenoid valve is connected to one end of the cutter bar lifting oil cylinder through the cutter bar lifting port by a pipeline. The third end of the cutter bar lifting solenoid valve is connected to the second oil return port through a pipeline. The first end of the cutter bar lowering solenoid valve is connected to the second hydraulic oil inlet port through a pipeline. The second end of the cutter bar lowering solenoid valve is connected to the other end of the cutter bar lifting oil cylinder through the cutter bar lowering port by a pipeline. The third end of the cutter bar lowering solenoid valve is connected to the second oil return port through a pipeline.

[0015] The beneficial effects of adopting the above further solution are as follows: When the header lift solenoid valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header forward tilt port and then enters the small chamber of the header lift cylinder to cause its piston rod to contract. Through the mechanical structure, the header is lifted. At this time, the hydraulic oil in the large chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. When the header lower solenoid valve and the header height maintaining solenoid valve are energized, the pressure oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out of the integrated hydraulic valve block through the header rearward tilt port and then enters the large chamber of the header lift cylinder to cause its piston rod to extend. Through the mechanical structure, the header is lowered. At this time, the hydraulic oil in the small chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. Due to the self-weight of the header, the hydraulic oil flowing into from the second hydraulic oil inlet only needs a relatively low pressure to lower the header.

[0016] Further, one end of the header lift cylinder is connected with a header height maintaining solenoid valve, and the header lift port is connected to one end of the header lift cylinder through the header height maintaining solenoid valve by pipeline.

[0017] The beneficial effects of adopting the above further solution are as follows: When the header lift solenoid valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header forward tilt port and then enters the small chamber of the header lift cylinder to cause its piston rod to contract. Through the mechanical structure, the header is lifted. At this time, the hydraulic oil in the large chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. When the header lower solenoid valve and the header height maintaining solenoid valve are energized, the pressure oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out of the integrated hydraulic valve block through the header rearward tilt port and then enters the large chamber of the header lift cylinder to cause its piston rod to extend. Through the mechanical structure, the header is lowered. At this time, the hydraulic oil in the small chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. Due to the self-weight of the header, the hydraulic oil flowing into from the second hydraulic oil inlet only needs a relatively low pressure to lower the header.

[0018] Further, the header tilting mechanism includes: a header forward tilt solenoid valve, a header rearward tilt solenoid valve, a header forward tilt port for connecting with the header tilt cylinder, a header rearward tilt port for connecting with the header tilt cylinder. The first end of the header forward tilt solenoid valve is connected to the first hydraulic oil inlet by pipeline, the second end of the header forward tilt solenoid valve is connected to one end of the header tilt cylinder through the header forward tilt port by pipeline, the third end of the header forward tilt solenoid valve is connected to the first oil return port by pipeline, the first end of the header rearward tilt solenoid valve is connected to the first hydraulic oil inlet by pipeline, the second end of the header rearward tilt solenoid valve is connected to the other end of the header tilt cylinder through the header rearward tilt port by pipeline, and the third end of the header rearward tilt solenoid valve is connected to the first oil return port by pipeline.

[0019] The beneficial effects of adopting the above further scheme are as follows: When the header tilting electromagnetic valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header tilting port and then enters the large chamber of the header tilting cylinder to make its piston rod extend. Through the mechanical structure, the header tilts forward. At this time, the hydraulic oil in the small chamber of the header tilting cylinder flows back to the hydraulic oil tank through the first oil return port. When the header tilting backward electromagnetic valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header tilting backward port and then enters the small chamber of the header tilting cylinder to make its piston rod contract. Through the mechanical structure, the header tilts backward. At this time, the hydraulic oil in the large chamber of the header tilting cylinder flows back to the hydraulic oil tank through the first oil return port.

[0020] Further, the header tilting mechanism further includes: a first check valve and a second check valve. The second end of the header tilting forward electromagnetic valve is connected to the header tilting forward port through the first check valve, and the first check valve is connected to the second end of the header tilting backward electromagnetic valve through a pipeline. The second end of the header tilting backward electromagnetic valve is connected to the header tilting backward port through the second check valve, and the second check valve is connected to the second end of the header tilting forward electromagnetic valve through a pipeline.

[0021] The beneficial effects of adopting the above further scheme are as follows: The setting of the check valve is used to prevent the reverse flow of pressure oil and improve the stability and reliability of the hydraulic system. When the header tilting forward electromagnetic valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header tilting forward port and then enters the large chamber of the header tilting cylinder to make its piston rod extend. Through the mechanical structure, the header tilts forward. At this time, the hydraulic oil in the small chamber of the header tilting cylinder flows back to the hydraulic oil tank through the first oil return port. When the header tilting backward electromagnetic valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header tilting backward port and then enters the small chamber of the header tilting cylinder to make its piston rod contract. Through the mechanical structure, the header tilts backward. At this time, the hydraulic oil in the large chamber of the header tilting cylinder flows back to the hydraulic oil tank through the first oil return port.

[0022] In addition, the present invention also provides a hydraulic control method for a self-propelled mowing and rolling machine. Based on the hydraulic system of a self-propelled mowing and rolling machine described in any one of the above, the hydraulic control method for a self-propelled mowing and rolling machine includes:

[0023] Controlling the header lifting cylinder, the header tilting cylinder, a plurality of flattening roller gap adjusting cylinders, and a pair of floating cylinders to work through the integrated hydraulic valve block.

[0024] The beneficial effects of the present invention are as follows: By designing the control method of the hydraulic system of the self-propelled mowing and flattening machine with the above floating oil cylinders, multiple groups of hydraulic control valves are integrated into the integrated hydraulic valve block, and the integrated hydraulic valve block is used to control the cutting table lifting cylinder, the cutting table tilting cylinder, multiple flattening roller gap adjusting cylinders, and a pair of floating oil cylinders to perform corresponding operations, which facilitates the operation of the hydraulic system, reduces the number of pump sources, improves the utilization rate of power components, avoids performance waste, and optimizes the overall machine cost. The pipeline structure is simplified, the hydraulic pipelines are reduced, the integration degree is improved, and it is convenient for the installation and maintenance of the hydraulic valve block. In addition, a proportional pressure reducing valve is newly added in the integrated hydraulic valve block. According to the feedback of the pressure sensor and by adjusting the proportional pressure reducing valve, the pressures of the flattening roller gap adjusting cylinder and the floating oil cylinder are adjusted, so that the floating profiling and the flattening roller gap adjustment are accurately controlled, and the reliability of the whole machine is improved.

[0025] Advantages of additional aspects of the present invention will be given in part in the following description, become apparent in part from the following description, or be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 It is a schematic structural diagram of the hydraulic system provided by an embodiment of the present invention.

[0027] Figure 2 It is one of the flow charts of the hydraulic control method provided by an embodiment of the present invention.

[0028] Figure 3 It is another flow chart of the hydraulic control method provided by an embodiment of the present invention.

[0029] Description of the attached reference numerals: 1. Integrated hydraulic valve block; 2. Header lift cylinder; 3. Header tilt cylinder; 4. Flattening roller gap adjustment cylinder; 5. Floating cylinder; 6. Inlet solenoid valve; 7. Header lifting mechanism; 8. Header tilting mechanism; 9. Flattening roller rolling pressure adjustment mechanism; 10. Header automatic profiling mechanism; 11. First hydraulic oil inlet; 12. Second hydraulic oil inlet; 13. First oil return port; 14. Second oil return port; 15. Proportional pressure reducing valve; 16. Brake solenoid valve; 17. Parking brake release port; 18. Flattening roller accumulator charging solenoid valve; 19. Flattening roller accumulator pressure relief solenoid valve; 20. Flattening roller rolling pressure adjustment port; 21. Flattening roller rolling accumulator; 22. Left floating cylinder; 23. Right floating cylinder; 24. Left floating accumulator charging solenoid valve; 25. Right floating accumulator charging solenoid valve; 26. Left floating accumulator pressure relief solenoid valve; 27. Right floating accumulator pressure relief solenoid valve; 28. Left header automatic profiling port; 29. Right header automatic profiling port; 30. Left floating accumulator; 31. Right floating accumulator; 32. Header lift solenoid valve; 33. Header lower solenoid valve; 34. Header lower port; 35. Header lift port; 36. Header height holding solenoid valve; 37. Header forward tilt solenoid valve; 38. Header rear tilt solenoid valve; 39. Header forward tilt port; 40. Header rear tilt port; 41. First check valve; 42. Second check valve. Detailed implementation manners

[0030] The principles and features of the present invention will be described below with reference to the accompanying drawings. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0031] As Figure 1 shown, an embodiment of the present invention provides a hydraulic system for a self-propelled mowing and flattening machine, which includes: an integrated hydraulic valve block 1, a header lift cylinder 2, a header tilt cylinder 3, a plurality of flattening roller gap adjustment cylinders 4, and a pair of floating cylinders 5. The header lift cylinder 2, the header tilt cylinder 3, the plurality of flattening roller gap adjustment cylinders 4, and the pair of floating cylinders 5 are all connected to the integrated hydraulic valve block 1 through pipelines.

[0032] The beneficial effects of the present invention are as follows: By designing a hydraulic system for a self-propelled mowing and flattening machine with an integrated hydraulic valve block, a header lift cylinder, a header tilt cylinder, a plurality of flattening roller gap adjustment cylinders, and a pair of floating cylinders, multiple sets of hydraulic control valves are integrated into the integrated hydraulic valve block, and the integrated hydraulic valve block is used to control the header lift cylinder, the header tilt cylinder, the plurality of flattening roller gap adjustment cylinders, and a pair of floating cylinders to perform corresponding operations, which is convenient for the operation of the hydraulic system, reduces the number of pump sources, improves the utilization rate of power components, avoids performance waste, and optimizes the overall machine cost. The pipeline structure is simplified, the hydraulic pipelines are reduced, the integration degree is improved, and it is convenient for the installation and maintenance of the hydraulic valve block.

[0033] The dashed box in the figure is an integrated hydraulic valve block.

[0034] Integrating multiple groups of hydraulic control valves simplifies the structure, reduces hydraulic pipelines, and improves the cost performance of the product; a proportional pressure reducing valve is newly added inside the valve, and the floating profiling control is precise, improving the reliability of the whole machine. In the embodiment of the present invention, the control of various functions of the self-propelled mower can be completed through a single valve; the single valve is an integrated hydraulic valve block. The proportional pressure reducing valve can be current-controlled or voltage-controlled, and its main function is to control the pressure behind the valve; pressure measuring ports are arranged at the flattening roller rolling adjustment port, the left cutter bar automatic profiling port, and the right cutter bar automatic profiling port on the integrated hydraulic valve block, and the pressure measuring ports are used to install sensors for monitoring pressure.

[0035] The following is a detailed description of the hydraulic working principle:

[0036] Cutter bar lifting function: Cutter bar rising: The inlet solenoid valve and the cutter bar lifting solenoid valve are energized. The pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block from the cutter bar forward tilt port and then enters the small chamber of the cutter bar lifting cylinder, causing its piston rod to contract. The cutter bar is lifted through a mechanical structure. At this time, the hydraulic oil in the large chamber of the cutter bar lifting cylinder flows back to the hydraulic oil tank through the second oil return port. Cutter bar descending: The cutter bar descending solenoid valve and the cutter bar height maintaining solenoid valve are energized. The pressure oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out of the integrated hydraulic valve block from the cutter bar rear tilt port and then enters the large chamber of the cutter bar lifting cylinder, causing its piston rod to extend. The cutter bar is lowered through a mechanical structure. At this time, the hydraulic oil in the small chamber of the cutter bar lifting cylinder flows back to the hydraulic oil tank through the second oil return port. Due to the self-weight of the cutter bar, the hydraulic oil flowing in from the second hydraulic oil inlet only needs a relatively low pressure to lower the cutter bar.

[0037] Cutter bar tilting function: Cutter bar forward tilt: The inlet solenoid valve and the cutter bar forward tilt solenoid valve are energized. The pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block from the cutter bar forward tilt port and then enters the large chamber of the cutter bar tilting cylinder, causing its piston rod to extend. The cutter bar is tilted forward through a mechanical structure. At this time, the hydraulic oil in the small chamber of the cutter bar tilting cylinder flows back to the hydraulic oil tank through the first oil return port. Cutter bar rear tilt: The inlet solenoid valve and the cutter bar rear tilt solenoid valve are energized. The pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block from the cutter bar rear tilt port and then enters the small chamber of the cutter bar tilting cylinder, causing its piston rod to contract. The cutter bar is tilted rearward through a mechanical structure. At this time, the hydraulic oil in the large chamber of the cutter bar tilting cylinder flows back to the hydraulic oil tank through the first oil return port.

[0038] Rolling pressure adjustment function of the flattening roller: The pressure-filled flattening roller pressure accumulator is connected to four gap adjustment cylinders of the flattening roller, forming an independent hydraulic flattening system. A pressure sensor is installed in this system to monitor the system pressure. According to different harvested crops and their growth conditions, this hydraulic flattening system requires different pressures. When it is necessary to increase the rolling pressure of the flattening roller, the oil inlet solenoid valve and the pressure charging solenoid valve of the flattening roller accumulator are energized. At this time, by adjusting the control current (or voltage) of the proportional pressure reducing valve, the outlet pressure of the proportional pressure reducing valve is changed, that is, the pressure charged into the hydraulic flattening system. During the pressure charging process, it is judged whether the target rolling pressure of the flattening roller is reached through the pressure value fed back by the pressure sensor and dynamic correction is carried out. After reaching the required pressure value, the pressure charging is completed. When it is necessary to reduce the rolling pressure of the flattening roller, the pressure relief solenoid valve of the flattening roller accumulator is energized, and the high-pressure oil in the hydraulic flattening system flows back to the hydraulic oil tank from the first oil return port.

[0039] Automatic profiling function of the cutter bar: When the self-propelled mowing and flattening machine is operating, it needs to float up and down according to the ground undulation. If the cutter bar is controlled to float up and down through the cutter bar lifting and lowering functions, the driver needs to highly concentrate and repeatedly issue cutter bar lifting and lowering commands, which is cumbersome to operate. The left floating accumulator and the right floating accumulator are connected to the large chambers of the left floating cylinder and the right floating cylinder to form an automatic profiling hydraulic system, which can realize the automatic profiling function of the cutter bar. In this system, the left floating cylinder and the right floating cylinder support both sides of the cutter bar through a mechanical structure. The pressure in the left floating accumulator and the right floating accumulator balances the self-weight of the cutter bar, so that the cutter bar floats on the ground. A pressure sensor is installed on both the left and right sides of this system to monitor the floating pressure on this side. According to different ground conditions, this system requires different floating pressures. Taking the adjustment of the left floating pressure as an example, when it is necessary to charge the left accumulator, the oil inlet solenoid valve and the left floating accumulator pressure charging solenoid valve are energized. At this time, by adjusting the control current (or voltage) of the proportional pressure reducing valve, the outlet pressure of the proportional pressure reducing valve is changed, that is, the pressure charged into the automatic profiling hydraulic system. During the pressure charging process, it is judged whether the target rolling pressure of the flattening roller is reached through the pressure value fed back by the pressure sensor and dynamic correction is carried out. After reaching the required pressure value, the pressure charging is completed. When it is necessary to relieve the pressure of the left accumulator, the left floating accumulator pressure relief solenoid valve is energized, and the hydraulic oil in the left automatic profiling hydraulic system flows back to the hydraulic oil tank from the first oil return port. Similarly, the floating pressure of the right automatic profiling hydraulic system can be adjusted in the same way, and the floating pressures on the left and right sides can be adjusted separately.

[0040] Release the parking brake: When it is necessary to release the parking brake, the brake solenoid valve is energized. The hydraulic oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out from the parking brake release port and then enters the wheel side reducer brake to release the parking brake. When the whole machine shuts down, the brake solenoid valve loses power and automatically enters the parking brake state.

[0041] As an alternative to the above hydraulic system, various functions can also be achieved through multiple pumps and multiple groups of hydraulic valves, and multiple groups of hydraulic control valves are integrated.

[0042] As Figure 1 shown, further, the integrated hydraulic valve block 1 includes: a header lifting mechanism 7, a header tilting mechanism 8, a flattening roller pressing adjustment mechanism 9, a header automatic profiling mechanism 10, a first hydraulic oil inlet 11, a second hydraulic oil inlet 12, a first oil return port 13 for connecting to a hydraulic oil tank, and a second oil return port 14 for connecting to a hydraulic oil tank. The header lifting mechanism 7, the header tilting mechanism 8, the flattening roller pressing adjustment mechanism 9, and the header automatic profiling mechanism 10 are all connected to the first hydraulic oil inlet 11 through pipelines. The header lifting mechanism 7 is connected to the second hydraulic oil inlet 12 through a pipeline. The header lifting mechanism 7, the header tilting mechanism 8, the flattening roller pressing adjustment mechanism 9, and the header automatic profiling mechanism 10 are all connected to the first oil return port 13 through pipelines. The header lifting mechanism 7 is connected to the second oil return port 14 through a pipeline. The header lifting mechanism 7 is connected to the header lifting oil cylinder 2 through a pipeline. The header tilting mechanism 8 is connected to the header tilting oil cylinder 3 through a pipeline. The flattening roller pressing adjustment mechanism 9 is respectively connected to a plurality of the flattening roller gap adjustment oil cylinders 4 through pipelines. The header automatic profiling mechanism 10 is respectively connected to a pair of the floating oil cylinders 5 through pipelines.

[0043] The beneficial effects of adopting the above further solution are as follows: The settings of the header lifting mechanism, the header tilting mechanism, the flattening roller pressing adjustment mechanism, the header automatic profiling mechanism, the first hydraulic oil inlet, the second hydraulic oil inlet, the first oil return port, and the second oil return port facilitate the manufacture of the integrated hydraulic valve block. Multiple groups of hydraulic control valves are integrated into the integrated hydraulic valve block, and the header lifting oil cylinder, the header tilting oil cylinder, a plurality of flattening roller gap adjustment oil cylinders, and a pair of floating oil cylinders are controlled through the integrated hydraulic valve block to perform corresponding operations, which is convenient for the operation of the hydraulic system, reduces the number of pump sources, improves the utilization rate of power components, avoids performance waste, and optimizes the overall machine cost. It simplifies the pipeline structure, reduces hydraulic pipelines, improves the integration degree, and is convenient for the installation and maintenance of the hydraulic valve block.

[0044] Among them, the flattening roller pressing adjustment mechanism 9 further includes: an inlet solenoid valve 6. The first end of the inlet solenoid valve 6 is connected to the first hydraulic oil inlet 11 through a pipeline. The second end of the inlet solenoid valve 6 is connected to the first oil return port through a pipeline. The first end of the left floating accumulator charging solenoid valve 24 is connected to the second end of the inlet solenoid valve 6 through a pipeline.

[0045] The inlet solenoid valve 6 is an enabling solenoid valve, which functions to control the on-off of the first hydraulic oil inlet 11 and the first oil return port 13. When the inlet solenoid valve 6 is de-energized, the hydraulic oil will flow from the first hydraulic oil inlet 11 through the inlet solenoid valve 6 directly into the first oil return port 13, without passing through the header lift solenoid valve 32, the header forward tilt solenoid valve 37, the header rearward tilt solenoid valve 38, the proportional pressure reducing valve 15, the flattening roller accumulator charging solenoid valve 18, the flattening roller accumulator pressure relief solenoid valve 19, the right floating accumulator charging solenoid valve 25, the right floating accumulator pressure relief solenoid valve 27, the left floating accumulator charging solenoid valve 24, and the left floating accumulator pressure relief solenoid valve 26; when the inlet solenoid valve 6 is energized, the hydraulic oil will not flow through the inlet solenoid valve 6, but can flow to the header lift solenoid valve 32, the header forward tilt solenoid valve 37, the header rearward tilt solenoid valve 38, the proportional pressure reducing valve 15, the flattening roller accumulator charging solenoid valve 18, the flattening roller accumulator pressure relief solenoid valve 19, the right floating accumulator charging solenoid valve 25, the right floating accumulator pressure relief solenoid valve 27, the left floating accumulator charging solenoid valve 24, and the left floating accumulator pressure relief solenoid valve 26, providing hydraulic oil for subsequent operations.

[0046] As Figure 1 shown, further, the integrated hydraulic valve block 1 further includes: a proportional pressure reducing valve 15, a brake solenoid valve 16, and a parking brake release port 17 for connecting to the wheel side reducer brake. The flattening roller pressing adjustment mechanism 9 and the header automatic profiling mechanism 10 are both connected to the first end of the proportional pressure reducing valve 15 through pipelines. The second end of the proportional pressure reducing valve 15 is connected to the first hydraulic oil inlet 11 through a pipeline. The third end of the proportional pressure reducing valve 15 is connected to the second oil return port 14 through a pipeline. The first end of the brake solenoid valve 16 is connected to the second hydraulic oil inlet 12 through a pipeline. The second end of the brake solenoid valve 16 is connected to the parking brake release port 17 through a pipeline. The third end of the brake solenoid valve 16 is connected to the second oil return port 14.

[0047] The beneficial effects of adopting the above further solution are as follows: A new proportional pressure reducing valve is added to the integrated hydraulic valve block, making the control of floating profiling and flattening roller gap adjustment precise and improving the reliability of the whole machine. When it is necessary to release the parking brake, the brake solenoid valve is energized, and the hydraulic oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out from the parking brake release port and then enters the wheel side reducer brake to release the parking brake. When the whole machine shuts down, the brake solenoid valve loses power and automatically enters the parking brake state.

[0048] As Figure 1As shown in the figure, further, the flattening roll rolling adjustment mechanism 9 includes: a flattening roll accumulator charging solenoid valve 18, a flattening roll accumulator pressure relief solenoid valve 19, and a flattening roll rolling adjustment port 21 for connecting with a plurality of the flattening roll gap adjustment cylinders 4. The first end of the flattening roll accumulator charging solenoid valve 18 is connected to the first hydraulic oil inlet 11 through a pipeline. The second end of the flattening roll accumulator charging solenoid valve 18 is connected to one end of the flattening roll accumulator pressure relief solenoid valve 19 through a pipeline. The other end of the flattening roll accumulator pressure relief solenoid valve 19 is connected to a plurality of the flattening roll gap adjustment cylinders 4 through the flattening roll rolling adjustment port 20. The third end of the flattening roll accumulator charging solenoid valve 18 is connected to the first end of the proportional pressure reducing valve 15 through a pipeline. A plurality of the flattening roll gap adjustment cylinders 4 are all connected with a flattening roll rolling accumulator 21. The flattening roll rolling adjustment port 20 is connected with a first pressure sensor, and the first pressure sensor is connected to the proportional pressure reducing valve 15.

[0049] The beneficial effects of adopting the above further scheme are as follows: The flattening roll rolling accumulator filled with pressure is connected to four flattening roll gap adjustment cylinders to form an independent hydraulic flattening system. A pressure sensor is installed in this system to monitor the system pressure. According to different harvested crops and their growth conditions, this hydraulic flattening system requires different pressures. When it is necessary to increase the rolling pressure of the flattening roll, the flattening roll accumulator charging solenoid valve is energized. At this time, the outlet pressure of the proportional pressure reducing valve is changed by adjusting the control current or voltage of the proportional pressure reducing valve, that is, the pressure charged into the hydraulic flattening system. During the charging process, it is judged whether the target rolling pressure of the flattening roll is reached through the pressure value fed back by the pressure sensor and dynamic correction is carried out. After reaching the required pressure value, the charging is completed. When it is necessary to reduce the rolling pressure of the flattening roll, the flattening roll accumulator pressure relief solenoid valve is energized, and the high-pressure oil in the hydraulic flattening system flows back to the hydraulic oil tank from the first oil return port.

[0050] Such as Figure 1As shown in the figure, further, a pair of floating oil cylinders 5 are a left floating oil cylinder 22 and a right floating oil cylinder 23. The header automatic profiling mechanism 10 includes: a left floating accumulator charging solenoid valve 24, a right floating accumulator charging solenoid valve 25, a left floating accumulator pressure relief solenoid valve 26, a right floating accumulator pressure relief solenoid valve 27, a left header automatic profiling port 28 for connecting with the left floating oil cylinder 22, and a right header automatic profiling port 29 for connecting with the right floating oil cylinder 23. The first end of the left floating accumulator charging solenoid valve 24 is connected to the first hydraulic oil inlet 11 through a pipeline. The second end of the left floating accumulator charging solenoid valve 24 is connected to one end of the left floating accumulator pressure relief solenoid valve 26 through a pipeline. The other end of the left floating accumulator pressure relief solenoid valve 26 is connected to the left floating oil cylinder 22 through the left header automatic profiling port 28. The third end of the left floating accumulator charging solenoid valve 24 is connected to the first end of the proportional pressure reducing valve 15 through a pipeline. The first end of the right floating accumulator charging solenoid valve 25 is connected to the first hydraulic oil inlet 11 through a pipeline. The second end of the right floating accumulator charging solenoid valve 25 is connected to one end of the right floating accumulator pressure relief solenoid valve 27 through a pipeline. The other end of the right floating accumulator pressure relief solenoid valve 27 is connected to the right floating oil cylinder 23 through the right header automatic profiling port 29. The third end of the right floating accumulator charging solenoid valve 25 is connected to the first end of the proportional pressure reducing valve 15 through a pipeline. The left floating oil cylinder 22 is connected with a left floating accumulator 30, and the right floating oil cylinder 23 is connected with a right floating accumulator 31. Second pressure sensors are installed on both the left header automatic profiling port 28 and the right header automatic profiling port 29, and the second pressure sensors are connected to the proportional pressure reducing valve 15.

[0051] The beneficial effects of adopting the above further solution are as follows: When the self-propelled mowing and rolling machine is operating, it needs to float up and down according to the ground undulation. If the up-and-down floating of the cutting table is controlled by the functions of lifting and lowering the cutting table, the driver needs to highly concentrate and repeatedly issue commands for lifting and lowering the cutting table, resulting in cumbersome operations. By connecting the left floating accumulator and the right floating accumulator to the large chambers of the left floating oil cylinder and the right floating oil cylinder, an automatic profiling hydraulic system can be formed to achieve the automatic profiling function of the cutting table. In this system, the left floating oil cylinder and the right floating oil cylinder support both sides of the cutting table through a mechanical structure, and the pressure in the left floating accumulator and the right floating accumulator balances the self-weight of the cutting table, enabling the cutting table to float on the ground. A pressure sensor is installed on both the left and right sides of this system to monitor the floating pressure on that side. According to different ground conditions, this system requires different floating pressures. Taking the adjustment of the floating pressure on the left side as an example, when it is necessary to pressurize the left floating accumulator, the charging solenoid valve of the left floating accumulator is energized. At this time, the outlet pressure of the proportional pressure reducing valve is changed by adjusting the control current or voltage of the proportional pressure reducing valve, that is, the pressure charged into the automatic profiling hydraulic system. During the pressurization process, it is judged whether the target flattening roller rolling pressure is reached and dynamically corrected through the pressure value fed back by the pressure sensor. After reaching the required pressure value, the pressurization is completed. When it is necessary to relieve the pressure of the left floating accumulator, the pressure relief solenoid valve of the left floating accumulator is energized, and the hydraulic oil in the left automatic profiling hydraulic system flows back to the hydraulic oil tank through the first oil return port. Similarly, the floating pressure of the right automatic profiling hydraulic system can be adjusted in the same way, and the floating pressures on the left and right sides can be adjusted separately.

[0052] As Figure 1 shown, further, the cutting table lifting mechanism 7 includes: a cutting table lifting solenoid valve 32, a cutting table lowering solenoid valve 33, a cutting table lowering port 34 for connecting with the cutting table lifting oil cylinder 2, and a cutting table lifting port 35 for connecting with the cutting table lifting oil cylinder 2. The first end of the cutting table lifting solenoid valve 32 is connected to the first hydraulic oil inlet 11 through a pipeline. The second end of the cutting table lifting solenoid valve 32 is connected to one end of the cutting table lifting oil cylinder 2 through the cutting table lifting port 35. The third end of the cutting table lifting solenoid valve 32 is connected to the second oil return port 14 through a pipeline. The first end of the cutting table lowering solenoid valve 33 is connected to the second hydraulic oil inlet 12 through a pipeline. The second end of the cutting table lowering solenoid valve 33 is connected to the other end of the cutting table lifting oil cylinder 2 through the cutting table lowering port 34. The third end of the cutting table lowering solenoid valve 33 is connected to the second oil return port 14 through a pipeline.

[0053] The beneficial effects of adopting the above further scheme are as follows: When the header lift solenoid valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block from the header forward tilt port and then enters the small chamber of the header lift cylinder to make its piston rod contract. Through the mechanical structure, the header is lifted. At this time, the hydraulic oil in the large chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. When the header lower solenoid valve and the header height maintaining solenoid valve are energized, the pressure oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out of the integrated hydraulic valve block from the header rear tilt port and then enters the large chamber of the header lift cylinder to make its piston rod extend. Through the mechanical structure, the header is lowered. At this time, the hydraulic oil in the small chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. Due to the self-weight of the header, the hydraulic oil flowing into from the second hydraulic oil inlet only needs a relatively low pressure to lower the header.

[0054] As Figure 1 shown, further, one end of the header lift cylinder 2 is connected with a header height maintaining solenoid valve 36, and the header lift port 35 is connected to one end of the header lift cylinder 2 through the header height maintaining solenoid valve 36 by pipeline.

[0055] The beneficial effects of adopting the above further scheme are as follows: When the header lift solenoid valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block from the header forward tilt port and then enters the small chamber of the header lift cylinder to make its piston rod contract. Through the mechanical structure, the header is lifted. At this time, the hydraulic oil in the large chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. When the header lower solenoid valve and the header height maintaining solenoid valve are energized, the pressure oil flowing into the integrated hydraulic valve block from the second hydraulic oil inlet flows out of the integrated hydraulic valve block from the header rear tilt port and then enters the large chamber of the header lift cylinder to make its piston rod extend. Through the mechanical structure, the header is lowered. At this time, the hydraulic oil in the small chamber of the header lift cylinder flows back to the hydraulic oil tank through the second oil return port. Due to the self-weight of the header, the hydraulic oil flowing into from the second hydraulic oil inlet only needs a relatively low pressure to lower the header.

[0056] As Figure 1As shown in the figure, further, the header tilting mechanism 3 includes: a header forward tilt solenoid valve 37, a header rearward tilt solenoid valve 38, a header forward tilt port 39 for connecting with the header tilt cylinder 3, and a header rearward tilt port 40 for connecting with the header tilt cylinder 3. The first end of the header forward tilt solenoid valve 37 is connected to the first hydraulic oil inlet 11 through a pipeline. The second end of the header forward tilt solenoid valve 37 is connected to one end of the header tilt cylinder 3 through the header forward tilt port 39 by a pipeline. The third end of the header forward tilt solenoid valve 37 is connected to the first oil return port 13 through a pipeline. The first end of the header rearward tilt solenoid valve 38 is connected to the first hydraulic oil inlet 11 through a pipeline. The second end of the header rearward tilt solenoid valve 38 is connected to the other end of the header tilt cylinder 3 through the header rearward tilt port 40 by a pipeline. The third end of the header rearward tilt solenoid valve 38 is connected to the first oil return port 13 through a pipeline.

[0057] The beneficial effects of adopting the above further solution are as follows: When the header forward tilt solenoid valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header forward tilt port and then enters the large chamber of the header tilt cylinder to make its piston rod extend, and the header tilts forward through the mechanical structure. At this time, the hydraulic oil in the small chamber of the header tilt cylinder flows back to the hydraulic oil tank through the first oil return port. When the header rearward tilt solenoid valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header rearward tilt port and then enters the small chamber of the header tilt cylinder to make its piston rod contract, and the header tilts rearward through the mechanical structure. At this time, the hydraulic oil in the large chamber of the header tilt cylinder flows back to the hydraulic oil tank through the first oil return port.

[0058] As Figure 1 As shown in the figure, further, the header tilting mechanism 3 further includes: a first check valve 41 and a second check valve 42. The second end of the header forward tilt solenoid valve 37 is connected to the header forward tilt port 39 through the first check valve 41 by a pipeline. The first check valve 41 is connected to the second end of the header rearward tilt solenoid valve 38 through a pipeline. The second end of the header rearward tilt solenoid valve 38 is connected to the header rearward tilt port 40 through the second check valve 42 by a pipeline. The second check valve 42 is connected to the second end of the header forward tilt solenoid valve 37 through a pipeline.

[0059] The beneficial effects of adopting the above further scheme are as follows: The setting of the one-way valve is used to prevent the reverse flow of pressure oil, improving the stability and reliability of the hydraulic system. When the header tilt solenoid valve is energized, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header tilt port and then enters the large chamber of the header tilt cylinder to make its piston rod extend. Through the mechanical structure, the header tilts forward. At this time, the hydraulic oil in the small chamber of the header tilt cylinder flows back to the hydraulic oil tank through the first oil return port. When the header tilts backward, the pressure oil flowing into the integrated hydraulic valve block from the first hydraulic oil inlet flows out of the integrated hydraulic valve block through the header tilt backward port and then enters the small chamber of the header tilt cylinder to make its piston rod contract. Through the mechanical structure, the header tilts backward. At this time, the hydraulic oil in the large chamber of the header tilt cylinder flows back to the hydraulic oil tank through the first oil return port.

[0060] As Figure 2 shown, in addition, the present invention also provides a hydraulic control method for a self-propelled mowing and rolling machine. Based on the hydraulic system of a self-propelled mowing and rolling machine described in any one of the above, the hydraulic control method of the self-propelled mowing and rolling machine includes:

[0061] S1. Control the operation of the header lift cylinder, header tilt cylinder, multiple flattening roller gap adjustment cylinders, and a pair of floating cylinders through the integrated hydraulic valve block.

[0062] As Figure 3 shown, the specific method for controlling the operation of the header lift cylinder, header tilt cylinder, multiple flattening roller gap adjustment cylinders, and a pair of floating cylinders through the integrated hydraulic valve block is as follows:

[0063] S11. When the header rises, control the header lift solenoid valve to be energized. The hydraulic oil flows from the first hydraulic oil inlet through the header lift solenoid valve, header lift port, and header height holding solenoid valve into one end of the header lift cylinder. The hydraulic oil at the other end of the header lift cylinder flows through the header lower solenoid valve into the second oil return port.

[0064] S12. When the header descends, control the header height holding solenoid valve and the header lower solenoid valve to be energized. The hydraulic oil flows from the second hydraulic oil inlet through the header lower solenoid valve, header lower port, and enters the other end of the header lift cylinder. The hydraulic oil at one end of the header lift cylinder flows through the header height holding solenoid valve and the header lift solenoid valve into the first oil return port.

[0065] S13. When the header tilts forward, control the header tilt solenoid valve to be energized. The hydraulic oil flows from the first hydraulic oil inlet through the header tilt solenoid valve and the header tilt port into one end of the header tilt cylinder. The hydraulic oil at the other end of the header tilt cylinder flows through the header tilt solenoid valve into the first oil return port.

[0066] S14. When the cutter bar tilts backward, control the cutter bar tilting solenoid valve to be energized. The hydraulic oil flows from the first hydraulic oil inlet through the cutter bar tilting solenoid valve, the cutter bar tilting port into the other end of the cutter bar tilting cylinder, and the hydraulic oil at one end of the cutter bar tilting cylinder flows through the cutter bar tilting solenoid valve into the first oil return port;

[0067] S15. When increasing the roller pressure of the flattening rollers, control the flattening roller accumulator pressurizing solenoid valve to be energized. The hydraulic oil flows from the first hydraulic oil inlet through the flattening roller accumulator pressurizing solenoid valve, the flattening roller accumulator pressure relief solenoid valve, the flattening roller pressure adjustment port into multiple flattening roller gap adjustment cylinders and the flattening roller pressure accumulator, and adjust the pressure at the first end of the proportional pressure reducing valve to control the pressure charged into the multiple flattening roller gap adjustment cylinders and the flattening roller pressure accumulator;

[0068] S16. When reducing the roller pressure of the flattening rollers, control the flattening roller accumulator pressure relief solenoid valve to be energized. The hydraulic oil in the multiple flattening roller gap adjustment cylinders and the flattening roller pressure accumulator flows through the flattening roller accumulator pressure relief solenoid valve, the flattening roller accumulator pressurizing solenoid valve into the first oil return port;

[0069] S17. When charging the left accumulator, control the left floating accumulator pressurizing solenoid valve to be energized. The hydraulic oil flows from the first hydraulic oil inlet through the left floating accumulator pressurizing solenoid valve, the left floating accumulator pressure relief solenoid valve, the left cutter bar automatic profiling port into the left floating cylinder and the left floating accumulator, and adjust the pressure at the first end of the proportional pressure reducing valve to control the pressure charged into the left floating cylinder and the left floating accumulator;

[0070] S18. When discharging the left accumulator, control the left floating accumulator pressure relief solenoid valve to be energized. The hydraulic oil in the left floating cylinder and the left floating accumulator flows through the left floating accumulator pressure relief solenoid valve, the left floating accumulator pressurizing solenoid valve into the first oil return port;

[0071] S19. When charging the right accumulator, control the right floating accumulator pressurizing solenoid valve to be energized. The hydraulic oil flows from the first hydraulic oil inlet through the right floating accumulator pressurizing solenoid valve, the right floating accumulator pressure relief solenoid valve, the right cutter bar automatic profiling port into the right floating cylinder and the right floating accumulator, and adjust the pressure at the first end of the proportional pressure reducing valve to control the pressure charged into the right floating cylinder and the right floating accumulator;

[0072] S110. When discharging the right accumulator, control the right floating accumulator pressure relief solenoid valve to be energized. The hydraulic oil in the right floating cylinder and the right floating accumulator flows through the right floating accumulator pressure relief solenoid valve, the right floating accumulator pressurizing solenoid valve into the first oil return port;

[0073] S111. When releasing the parking brake, control the brake solenoid valve to be energized. The hydraulic oil flows from the second hydraulic oil inlet through the brake solenoid valve, the parking brake release port into the wheel side reducer brake to release the parking brake;

[0074] S112. When parking braking, control the braking solenoid valve to lose power to enter the parking braking state.

[0075] The beneficial effects of the present invention are as follows: By designing the control method of the hydraulic system of the self-propelled mowing and flattening machine with the above floating oil cylinders, a plurality of hydraulic control valves are integrated into an integrated hydraulic valve block, and the integrated hydraulic valve block is used to control the cutting table lifting cylinder, the cutting table tilting cylinder, a plurality of flattening roller gap adjusting cylinders and a pair of floating oil cylinders to perform corresponding operations, which facilitates the operation of the hydraulic system, reduces the number of pump sources, improves the utilization rate of power components, avoids performance waste, and optimizes the overall machine cost. The pipeline structure is simplified, the hydraulic pipelines are reduced, the integration degree is improved, and it is convenient for the installation and maintenance of the hydraulic valve block. In addition, a proportional pressure reducing valve is newly added in the integrated hydraulic valve block. According to the feedback of the pressure sensor and by adjusting the proportional pressure reducing valve, the pressures of the flattening roller gap adjusting cylinder and the floating oil cylinder are adjusted, so that the floating profiling and the flattening roller gap adjustment are accurately controlled, and the reliability of the whole machine is improved.

[0076] Finally, it should be noted that: The above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit them; Although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that: They can still modify the technical solutions recorded in the foregoing embodiments, or equivalently replace some or all of the technical features; And these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A hydraulic system for a self-propelled mower and crimper, characterized in that, Including: An integrated hydraulic valve block (1), a header lift cylinder (2), a header tilt cylinder (3), a plurality of flattening roll gap adjustment cylinders (4), and a pair of floating cylinders (5). The header lift cylinder (2), the header tilt cylinder (3), the plurality of flattening roll gap adjustment cylinders (4), and the pair of floating cylinders (5) are all connected to the integrated hydraulic valve block (1) through pipelines. The integrated hydraulic valve block (1) includes: a header lifting mechanism (7), a header tilting mechanism (8), a flattening roll pressing adjustment mechanism (9), a header automatic profiling mechanism (10), a first hydraulic oil inlet (11), a second hydraulic oil inlet (12), a first oil return port (13) for connecting to a hydraulic oil tank, and a second oil return port (14) for connecting to a hydraulic oil tank. The header lifting mechanism (7), the header tilting mechanism (8), the flattening roll pressing adjustment mechanism (9), and the header automatic profiling mechanism (10) are all connected to the first hydraulic oil inlet (11) through pipelines. The header lifting mechanism (7) is connected to the second hydraulic oil inlet (12) through a pipeline. The header lifting mechanism (7), the header tilting mechanism (8), the flattening roll pressing adjustment mechanism (9), and the header automatic profiling mechanism (10) are all connected to the first oil return port (13) through pipelines. The header lifting mechanism (7) is connected to the second oil return port (14) through a pipeline. The header lifting mechanism (7) is connected to the header lift cylinder (2) through a pipeline. The header tilting mechanism (8) is connected to the header tilt cylinder (3) through a pipeline. The flattening roll pressing adjustment mechanism (9) is respectively connected to the plurality of flattening roll gap adjustment cylinders (4) through pipelines. The header automatic profiling mechanism (10) is respectively connected to the pair of floating cylinders (5) through pipelines. The integrated hydraulic valve block (1) further includes: a proportional pressure reducing valve (15), a brake solenoid valve (16), and a parking brake release port (17) for connecting to a wheel side reducer brake. The flattening roll pressing adjustment mechanism (9) and the header automatic profiling mechanism (10) are both connected to the first end of the proportional pressure reducing valve (15) through pipelines. The second end of the proportional pressure reducing valve (15) is connected to the first hydraulic oil inlet (11) through a pipeline. The third end of the proportional pressure reducing valve (15) is connected to the second oil return port (14) through a pipeline. The first end of the brake solenoid valve (16) is connected to the second hydraulic oil inlet (12) through a pipeline. The second end of the brake solenoid valve (16) is connected to the parking brake release port (17) through a pipeline. The third end of the brake solenoid valve (16) is connected to the second oil return port (14).

2. The hydraulic system of a self-propelled mowing and rolling machine according to claim 1, characterized in that, The flattening roll rolling adjustment mechanism (9) includes: a flattening roll accumulator charging solenoid valve (18), a flattening roll accumulator pressure relief solenoid valve (19), and a flattening roll rolling adjustment port (20) for connecting with a plurality of the flattening roll gap adjustment cylinders (4). The first end of the flattening roll accumulator charging solenoid valve (18) is connected to the first hydraulic oil inlet (11) through a pipeline. The second end of the flattening roll accumulator charging solenoid valve (18) is connected to one end of the flattening roll accumulator pressure relief solenoid valve (19) through a pipeline. The other end of the flattening roll accumulator pressure relief solenoid valve (19) is connected to a plurality of the flattening roll gap adjustment cylinders (4) through the flattening roll rolling adjustment port (20) by a pipeline. The third end of the flattening roll accumulator charging solenoid valve (18) is connected to the first end of the proportional pressure reducing valve (15) through a pipeline. A plurality of the flattening roll gap adjustment cylinders (4) are all connected with a flattening roll rolling accumulator (21). The flattening roll rolling adjustment port (20) is connected with a first pressure sensor, and the first pressure sensor is connected to the proportional pressure reducing valve (15).

3. The hydraulic system of a self-propelled mowing and rolling machine according to claim 1, characterized in that, The pair of floating oil cylinders (5) are a left floating oil cylinder (22) and a right floating oil cylinder (23). The header automatic profiling mechanism (10) includes: a left floating accumulator charging solenoid valve (24), a right floating accumulator charging solenoid valve (25), a left floating accumulator pressure relief solenoid valve (26), a right floating accumulator pressure relief solenoid valve (27), a left header automatic profiling port (28) for connecting with the left floating oil cylinder (22), and a right header automatic profiling port (29) for connecting with the right floating oil cylinder (23). The first end of the left floating accumulator charging solenoid valve (24) is connected to the first hydraulic oil inlet (11) through a pipeline. The second end of the left floating accumulator charging solenoid valve (24) is connected to one end of the left floating accumulator pressure relief solenoid valve (26) through a pipeline. The other end of the left floating accumulator pressure relief solenoid valve (26) is connected to the left floating oil cylinder (22) through the left header automatic profiling port (28) by a pipeline. The third end of the left floating accumulator charging solenoid valve (24) is connected to the first end of the proportional pressure reducing valve (15) through a pipeline. The first end of the right floating accumulator charging solenoid valve (25) is connected to the first hydraulic oil inlet (11) through a pipeline. The second end of the right floating accumulator charging solenoid valve (25) is connected to one end of the right floating accumulator pressure relief solenoid valve (27) through a pipeline. The other end of the right floating accumulator pressure relief solenoid valve (27) is connected to the right floating oil cylinder (23) through the right header automatic profiling port (29) by a pipeline. The third end of the right floating accumulator charging solenoid valve (25) is connected to the first end of the proportional pressure reducing valve (15) through a pipeline. The left floating oil cylinder (22) is connected to a left floating accumulator (30), and the right floating oil cylinder (23) is connected to a right floating accumulator (31). Second pressure sensors are installed at both the left header automatic profiling port (28) and the right header automatic profiling port (29), and the second pressure sensors are connected to the proportional pressure reducing valve (15).

4. The hydraulic system of a self-propelled mowing and flattening machine according to claim 1, characterized in that, The header lifting mechanism (7) includes: a header lifting solenoid valve (32), a header lowering solenoid valve (33), a header lowering port (34) for connecting with the header lifting oil cylinder (2), and a header lifting port (35) for connecting with the header lifting oil cylinder (2). The first end of the header lifting solenoid valve (32) is connected to the first hydraulic oil inlet (11) through a pipeline. The second end of the header lifting solenoid valve (32) is connected to one end of the header lifting oil cylinder (2) through the header lifting port (35) by a pipeline. The third end of the header lifting solenoid valve (32) is connected to the second oil return port (14) through a pipeline. The first end of the header lowering solenoid valve (33) is connected to the second hydraulic oil inlet (12) through a pipeline. The second end of the header lowering solenoid valve (33) is connected to the other end of the header lifting oil cylinder (2) through the header lowering port (34) by a pipeline. The third end of the header lowering solenoid valve (33) is connected to the second oil return port (14) through a pipeline.

5. The hydraulic system of a self-propelled mowing and rolling machine according to claim 4, characterized in that, One end of the header lifting oil cylinder (2) is connected with a header height maintaining solenoid valve (36), and the header lifting port (35) is connected to one end of the header lifting oil cylinder (2) through the header height maintaining solenoid valve (36) by pipeline.

6. The hydraulic system of a self-propelled mowing and rolling machine according to claim 1, characterized in that, The header tilting mechanism (8) includes: a header forward tilting solenoid valve (37), a header rearward tilting solenoid valve (38), a header forward tilting port (39) for connecting with the header tilting oil cylinder (3), a header rearward tilting port (40) for connecting with the header tilting oil cylinder (3). The first end of the header forward tilting solenoid valve (37) is connected to the first hydraulic oil inlet (11) by pipeline. The second end of the header forward tilting solenoid valve (37) is connected to one end of the header tilting oil cylinder (3) through the header forward tilting port (39) by pipeline. The third end of the header forward tilting solenoid valve (37) is connected to the first oil return port (13) by pipeline. The first end of the header rearward tilting solenoid valve (38) is connected to the first hydraulic oil inlet (11) by pipeline. The second end of the header rearward tilting solenoid valve (38) is connected to the other end of the header tilting oil cylinder (3) through the header rearward tilting port (40) by pipeline. The third end of the header rearward tilting solenoid valve (38) is connected to the first oil return port (13) by pipeline.

7. The hydraulic system of a self-propelled mowing and rolling machine according to claim 6, characterized in that, The header tilting mechanism (8) further includes: a first check valve (41) and a second check valve (42). The second end of the header forward tilting solenoid valve (37) is connected to the header forward tilting port (39) through the first check valve (41) by pipeline. The first check valve (41) is connected to the second end of the header rearward tilting solenoid valve (38) by pipeline. The second end of the header rearward tilting solenoid valve (38) is connected to the header rearward tilting port (40) through the second check valve (42) by pipeline. The second check valve (42) is connected to the second end of the header forward tilting solenoid valve (37) by pipeline.

8. A hydraulic control method for a self-propelled mowing and rolling machine, characterized in that, Based on the hydraulic system of a self-propelled mowing and rolling machine according to any one of the above claims 1 to 7, the hydraulic control method of the self-propelled mowing and rolling machine includes: Controlling the operation of the header lifting oil cylinder, the header tilting oil cylinder, multiple flattening roller gap adjusting oil cylinders and a pair of floating oil cylinders through an integrated hydraulic valve block.

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