Seeder fan driving hydraulic system and seeder

Abstract

The invention relates to a seeder fan driving hydraulic system which comprises a motor and a fan and further comprises an oil tank, a driving pump, a driving pump control valve and a gear pump, the driving pump comprises an oil supplementing overflow valve set and a variable pump which are both provided with an oil inlet m and an oil outlet n, and the oil outlet n of the gear pump is communicated with the oil supplementing overflow valve set and the oil inlet m of the driving pump control valve at the same time; an oil outlet n of the oil supplementing overflow valve set is communicated with the variable pump, an oil inlet m of the motor and the oil tank at the same time, an oil outlet n of the variable pump is communicated with the oil inlet m of the motor, an oil outlet of the motor is further communicated with the oil inlet m of the variable pump, the driving pump control valve is communicated with the variable pump, and the driving pump control valve and the variable pump are both communicated with the oil tank. By the adoption of the technical scheme, the technical problems that the wind speed and the wind pressure of an existing seeder fan are poor in accurate control degree, and stability is poor can be solved.

Description

Technical Field

[0001] The present invention relates to the technical field of seeders, and particularly to a hydraulic system for driving a blower of a seeder and a seeder. Background Art

[0002] In the prior art, the blower of a seeder is usually driven by a hydraulic motor, and the power of the hydraulic motor comes from a hydraulic pump in the hydraulic system of the seeder. The hydraulic pump converts mechanical energy into hydraulic energy. The hydraulic pump extracts hydraulic oil from the fuel tank of the tractor, pressurizes it, and transports it to the hydraulic motor through a pipeline. The hydraulic motor then drives the blower to operate. In this process, the hydraulic oil in the tractor fuel tank needs to be supplied to components such as the engine at the same time, resulting in an unstable supply to the blower hydraulic motor, being unable to precisely control the wind speed and wind pressure of the blower, and making the wind speed and wind pressure of the blower unable to be kept stable. Summary of the Invention

[0003] Aiming at the technical problems that the wind speed and wind pressure of the existing seeder blower have poor precision control and poor stability, the present invention provides a hydraulic system for driving a seeder blower and a seeder.

[0004] The technical solution of the present invention to solve the above technical problems is as follows:

[0005] The present invention provides a hydraulic system for driving a seeder blower, including a motor having an oil inlet m and an oil outlet n and a blower drivingly connected to the output shaft of the motor, and further including a fuel tank, a driving pump, a driving pump control valve, and a gear pump having an oil inlet m and an oil outlet n. The driving pump includes a make-up overflow valve group and a variable pump both having an oil inlet m and an oil outlet n. The oil outlet n of the gear pump is simultaneously connected to the make-up overflow valve group and the oil inlet m of the driving pump control valve. The oil outlet n of the make-up overflow valve group is simultaneously connected to the variable pump, the oil inlet m of the motor, and the fuel tank. The oil outlet n of the variable pump is connected to the oil inlet m of the motor. The oil outlet of the motor is also connected to the oil inlet m of the variable pump. The driving pump control valve is connected to the variable pump. Both the driving pump control valve and the variable pump are connected to the fuel tank.

[0006] The beneficial effect of the present invention is: By adopting the above driving method, the gear pump pumps pressure oil, and the driving pump and the driving pump control valve are used to adjust and control the pressure oil quantity, so as to improve the technical problems that the wind speed and wind pressure of the existing seeder blower have poor precision control and poor stability.

[0007] On the basis of the above technical solution, the present invention can also be improved as follows.

[0008] Further, the variable pump includes a variable pump body having an oil inlet m and an oil outlet n, and a variable plunger having a left oil chamber a and a right oil chamber b. The oil inlet m of the variable pump body communicates with the oil outlet n of the motor. The variable plunger is connected to the swash plate of the variable pump body. The drive pump control valve is connected to both the variable plunger and the variable pump body, and the left oil chamber a of the variable plunger communicates with the fuel tank through the drive pump control valve.

[0009] The beneficial effect of adopting the above further solution is that when the fan is in operation, under the action of the gear pump, oil is delivered to the right oil chamber b of the variable plunger. The plunger of the variable plunger moves and changes the displacement of the variable pump body, continuously outputting high-pressure oil.

[0010] Further, the oil replenishing and overflow valve group includes a first safety valve and a second safety valve both having an oil inlet m and an oil outlet n. The oil outlet n of the gear pump communicates with the oil inlets m of both the first safety valve and the second safety valve at the same time. The oil outlet n of the first safety valve communicates with the fuel tank and the oil inlet m of the motor at the same time. The oil outlet n of the second safety valve communicates with the fuel tank and the oil inlet m of the variable pump at the same time.

[0011] The beneficial effect of adopting the above further solution is that when the fan is in operation and during the oil pumping process, the gear pump pumps the pressure oil to the oil inlets m of the first safety valve and the second safety valve. The pressure oil is pumped to the motor through the oil outlet n of the first safety valve. The pressure oil is delivered to the oil inlet m of the variable pump through the oil outlet n of the second safety valve, and then is delivered to the motor through the oil outlet n of the variable pump, realizing the operation of the motor, driving the rotation of the fan, generating a certain negative pressure value for seeding operations.

[0012] Further, the oil replenishing and overflow valve group further includes an overflow valve having an oil inlet m and an oil outlet n. The oil inlet m of the overflow valve communicates with the oil outlet n of the gear pump. The oil outlet n of the overflow valve communicates with the fuel tank. The overflow valve, the first safety valve, and the second safety valve are arranged in parallel.

[0013] The beneficial effect of adopting the above further solution is that in the oil replenishing standby state, when the fan starts, the gear pump transports the hydraulic oil to the drive pump through the pipeline, and then delivers the oil to the pipeline through the first safety valve and the second safety valve respectively. When the oil pressure rises to the required value and reaches the set value of the overflow valve, the overflow valve opens, returning the excess oil to the fuel tank, maintaining this pressure value, realizing the replenishment of the oil in the pipeline, maintaining low oil pressure operation, and waiting for the subsequent commands of the system.

[0014] Further, the drive pump control valve includes a first proportional solenoid valve, a second proportional solenoid valve, a spool plunger, and a variable spool. Both the first proportional solenoid valve and the second proportional solenoid valve have an oil inlet m and an oil outlet n. The spool plunger has a left oil chamber e and a right oil chamber f. The variable spool has a left oil chamber c and a right oil chamber d. The oil outlet n of the first proportional solenoid valve communicates with the left oil chamber e of the spool plunger. The oil outlet n of the second proportional solenoid valve communicates with the right oil chamber f of the spool plunger. And the spool plunger is connected to the variable spool. The variable spool is also connected to the variable pump at the same time. The oil outlet n of the gear pump communicates with the oil inlets m of both the first proportional solenoid valve and the second proportional solenoid valve, and communicates with the variable pump through the right oil chamber d of the variable spool. And the variable pump communicates with the fuel tank through the right oil chamber d of the variable spool.

[0015] The beneficial effect of adopting the above further solution is: When the fan is in operation and during the oil pumping process, the second proportional solenoid valve is electrified. The gear pump pumps the pressure oil in the fuel tank and delivers it to the oil inlet m of the second proportional solenoid valve, and then through the oil outlet n of the second proportional solenoid valve to the right oil chamber f of the spool plunger, forcing it to move the spool that drives the variable spool. At the same time, the gear pump pumps the pressure oil to the right oil chamber d of the variable spool. The oil pressure is then delivered to the variable pump and continuously outputs high-pressure oil through the variable pump. At this time, the gear pump pumps the pressure oil to the oil inlet m of the oil replenishing and overflow valve group. The pressure oil is pumped to the motor through the oil outlet n of the oil replenishing and overflow valve group. The pressure oil is delivered to the oil inlet m of the variable pump through the oil outlet n of the oil replenishing and overflow valve group, and then is delivered to the motor through the oil outlet n of the variable pump, realizing the operation of the motor, driving the rotation of the fan, generating a certain negative pressure value for seeding operations.

[0016] Further, both the first proportional solenoid valve and the second proportional solenoid valve have an oil drain port L, and both of the oil drain ports L communicate with the fuel tank.

[0017] The beneficial effect of adopting the above further solution is: When the system pressure is too high, the oil is delivered back to the fuel tank through this oil drain port L to ensure the smooth return of the oil, avoid the influence of back pressure on the system, and protect the hydraulic system from overpressure damage.

[0018] Further, the oil outlet n of the first proportional solenoid valve, the oil outlet n of the second proportional solenoid valve, and the left oil chamber e and the right oil chamber f of the spool plunger all communicate with the fuel tank.

[0019] The beneficial effect of adopting the above further solution is: To provide an oil return path for the first proportional solenoid valve, the second proportional solenoid valve, and the spool plunger, and return the excess oil to the fuel tank.

[0020] Further, it further includes a wind pressure sensor and a controller communicatively connected to the wind pressure sensor. The wind pressure sensor is disposed on the fan, and the controller is further connected to the drive pump control valve. The controller includes a display module.

[0021] The beneficial effect of adopting the above further solution is that: when the fan is in operation, the negative pressure value generated by the rotation of the fan can be monitored in real time through the wind pressure sensor, and the monitored value is transmitted to the controller. The controller displays this value in real time through the display module. The operator can manually adjust the input current value of the drive pump control valve based on this value. After the negative pressure value is adjusted to an appropriate value, the operation can be stopped, and the seeder can operate normally.

[0022] Further, it further includes a rotational speed sensor communicatively connected to the controller. The rotational speed sensor is used to detect the shaft rotational speed of the motor to obtain a real-time rotational speed value x. When the real-time rotational speed value x is lower than a threshold value y, the controller adjusts the current value of the drive pump control valve.

[0023] The beneficial effect of adopting the above further solution is that: when the fan is in operation, the shaft rotational speed of the motor can be monitored in real time through the rotational speed sensor to obtain a real-time rotational speed value x, and it is transmitted to the controller.

[0024] Further, it further includes a first bypass valve having an oil inlet m and an oil outlet n. The oil inlet m of the first bypass valve is communicated with the oil outlet n of the motor, and the oil outlet n of the first bypass valve is communicated with the oil inlet m of the motor.

[0025] The beneficial effect of adopting the above further solution is that: after the fan drive stops, the fan will continue to drive the motor to rotate due to its own inertia, which will generate a certain high-pressure oil at the position of the oil outlet n of the motor. The first bypass valve can prevent the pressure from being too high, which may cause oil dispersion and pipeline failures. The excessive pressure oil can reach the oil inlet m of the motor through the first bypass valve, and the motor itself can generate a circulation of the oil until it stops rotating, achieving the purpose of shutdown buffering.

[0026] Further, it further includes a hydraulic oil radiator having an oil inlet m and an oil outlet n. The oil inlet m of the hydraulic oil radiator is communicated with the oil outlet n of the motor, and the oil outlet n of the hydraulic oil radiator is communicated with the oil inlet m of the variable pump.

[0027] The beneficial effects of adopting the above further solution are as follows: When the fan is in operation, high-pressure oil reaches the motor through the pipeline, and the return oil returns to the oil inlet m of the variable pump body of the variable pump after being cooled by the hydraulic oil radiator, so as to reduce the temperature of the high-pressure oil through the hydraulic oil radiator, effectively prevent the hydraulic oil from deteriorating or being damaged due to excessive temperature, maintain the performance of the hydraulic oil, improve the system efficiency and reliability, prevent leakage, ensure the normal operation of the hydraulic system, extend the service life of the equipment, and also contribute to energy conservation and environmental protection.

[0028] Furthermore, it also includes a filter and a pressure filter both having an oil inlet m and an oil outlet n. The oil inlet m of the filter is connected to the fuel tank, and the oil outlet n is connected to the oil inlet m of the gear pump. The oil inlet m of the pressure filter is connected to the oil outlet n of the gear pump, and the oil outlet n is simultaneously connected to the oil inlet m of the oil replenishing overflow valve group and the driving pump control valve.

[0029] The beneficial effects of adopting the above further solution are as follows: It can filter impurities and particles in the oil entering the gear pump through the filter, prevent these impurities from entering the pump, thereby protecting the internal parts of the gear pump and avoiding wear and blockage; and filter the oil after being pressurized by the gear pump through the pressure filter to further remove impurities in the oil and ensure that the oil remains clean during transportation.

[0030] The present invention also provides a seeder, including the seeder fan-driven hydraulic system described above. Description of the Drawings

[0031] Figure 1 It is a schematic diagram of the seeder fan-driven hydraulic system of the present invention;

[0032] Figure 2 For the present invention Figure 1 Partial enlarged view;

[0033] Figure 3 It is a schematic diagram of the seeder fan-driven hydraulic system of the present invention in the oil replenishing standby state;

[0034] Figure 4 For the present invention Figure 3 Partial enlarged view;

[0035] Figure 5 It is a schematic diagram of the seeder fan-driven hydraulic system of the present invention in the fan running state;

[0036] Figure 6 For the present invention Figure 5 Partial enlarged view;

[0037] Figure 7 It is a schematic diagram of the seeder fan-driven hydraulic system of the present invention in the manual and automatic mode states;

[0038] Figure 8 For the present invention Figure 7 A partial enlarged view of

[0039] Figure 9 The present invention is a schematic diagram of the blower driving hydraulic system of the seed drill in the shutdown buffer state.

[0040] In the accompanying drawings, the components represented by the reference numerals are listed as follows:

[0041] 1. Filter; 2. Gear pump; 3. Pressure filter; 4. Drive pump; 41. Variable pump body; 42. Variable plunger; 43. First safety valve; 44. Second safety valve; 45. Overflow valve; 5. Drive pump control valve; 51. First proportional solenoid valve; 52. Second proportional solenoid valve; 53. Valve core plunger; 54. Variable valve core; 6. Hydraulic oil radiator; 61. Second bypass valve; 7. First bypass valve; 8. Motor; 9. Fan; 10. Wind pressure sensor; 11. Speed ​​sensor; 12. Controller; 13. Oil tank. DETAILED DESCRIPTION

[0042] The principles and features of the present invention are described below. The examples given are only used to explain the present invention and are not used to limit the scope of the present invention.

[0043] Example 1

[0044] like Figures 1 to 9 The present invention provides a hydraulic system for driving a blower of a seed drill, comprising a motor 8 having an oil inlet m and an oil outlet n and a blower 9 drivingly connected to an output shaft of the motor 8, and further comprising an oil tank 13, a driving pump 4, a driving pump control valve 5, and a gear pump 2 having an oil inlet m and an oil outlet n. The driving pump 4 comprises an oil replenishment overflow valve group and a variable pump, both of which have an oil inlet m and an oil outlet n. The oil outlet n of the gear pump 2 is simultaneously connected to the oil inlet m of the oil replenishment overflow valve group and the driving pump control valve 5. The oil outlet n of the oil replenishment overflow valve group is simultaneously connected to the variable pump, the oil inlet m of the motor 8, and the oil tank 13. The oil outlet n of the variable pump is connected to the oil inlet m of the motor 8. The oil outlet of the motor 8 is also connected to the oil inlet m of the variable pump. The driving pump control valve 5 is connected to the variable pump. The driving pump control valve 5 and the variable pump are both connected to the oil tank 13.

[0045] The beneficial effect of this embodiment is: by adopting the above-mentioned driving method, the pressure oil is pumped by the gear pump 2, and the drive pump 4 and the drive pump control valve 5 are used to adjust and control the amount of pressure oil, so as to improve the technical problems of poor precision control and poor stability of the wind speed and wind pressure of the existing seed drill fan 9.

[0046] When the fan 9 is in operation and during the pump oil process, the drive pump control valve is electrified. The gear pump 2 pumps the pressure oil from the fuel tank 13 and delivers it to the oil inlet m of the drive pump control valve 5. It is then delivered to the variable pump through the oil outlet n of the drive pump control valve 5, causing the displacement of the variable pump to change and continuously output high-pressure oil. At this time, the gear pump 2 pumps the pressure oil to the oil inlet m of the oil replenishing overflow valve group. The pressure oil is pumped to the motor 8 through the oil outlet n of the oil replenishing overflow valve group, and is also delivered to the oil inlet m of the variable pump and then to the motor 8 through the oil outlet n of the variable pump, enabling the operation of the motor 8, driving the rotation of the fan 9, generating a certain negative pressure value for seeding operations.

[0047] During the oil return process, the pressure oil returns from the oil outlet n of the motor 8 to the oil inlet m of the variable pump to achieve circulation, while the oil in the variable pump is delivered back to the fuel tank 13.

[0048] During this process, the oil replenishing overflow valve group can deliver the excess oil back to the fuel tank 13 through its oil outlet n to maintain the safety of the entire oil circuit system.

[0049] Based on the above embodiments, the motor 8 also has an oil drain port L. The motor 8 is connected to the fuel tank 13 through the oil drain port L to prevent the pressure in the motor 8 housing from being too high and at the same time discharge the high-temperature oil, playing a role in cooling the motor 8.

[0050] Embodiment 2

[0051] As Figure 1 and Figure 2 , based on Embodiment 1, the variable pump includes a variable pump body 41 with an oil inlet m and an oil outlet n and a variable plunger 42 with a left oil chamber a and a right oil chamber b. The oil inlet m of the variable pump body 41 is connected to the oil outlet n of the motor 8. The variable plunger 42 is connected to the swash plate of the variable pump body 41. The drive pump control valve 5 is connected to both the variable plunger 42 and the variable pump body 41, and the left oil chamber a of the variable plunger 42 is connected to the fuel tank 13 through the drive pump control valve 5.

[0052] The beneficial effect of adopting the preferred solution in the above embodiments is that when the fan 9 is in operation, under the action of the gear pump 2, the oil is delivered to the right oil chamber b of the variable plunger 42, and the plunger of the variable plunger 42 moves to change the displacement of the variable pump body 41, continuously outputting high-pressure oil.

[0053] During the oil return process, the pressure oil returns from the oil outlet n of the motor 8 to the oil inlet m of the variable pump body 41 to achieve circulation, while the oil in the left oil chamber a of the variable plunger 42 is delivered back to the fuel tank 13 through the drive pump control valve 5.

[0054] Among them, the variable plunger 42 is connected to the swash plate of the variable pump body 41 through a connecting rod.

[0055] Embodiment 3

[0056] As Figure 1 and Figure 2 Based on Embodiments 1-2, the oil replenishing and overflow valve group includes a first safety valve 43 and a second safety valve 44 both having an oil inlet m and an oil outlet n. The oil outlet n of the gear pump 2 is simultaneously connected to the oil inlets m of the first safety valve 43 and the second safety valve 44. The oil outlet n of the first safety valve 43 is simultaneously connected to the oil tank 13 and the oil inlet m of the motor 8. The oil outlet n of the second safety valve 44 is simultaneously connected to the oil tank 13 and the oil inlet m of the variable pump.

[0057] The beneficial effect of adopting the preferred solution in the above embodiments is that when the fan 9 is in operation and during the oil pumping process, the gear pump 2 pumps the pressurized oil to the oil inlets m of the first safety valve 43 and the second safety valve 44. The pressurized oil is pumped to the motor 8 through the oil outlet n of the first safety valve 43. The pressurized oil is transported to the oil inlet m of the variable pump through the oil outlet n of the second safety valve 44, and then is transported to the motor 8 through the oil outlet n of the variable pump, realizing the operation of the motor 8, driving the rotation of the fan 9, generating a certain negative pressure value for seeding operations.

[0058] During this process, the first safety valve 43 and the second safety valve 44 can transport the excess oil back to the oil tank 13 through their oil outlets n to maintain the safety of the entire oil circuit system.

[0059] Based on the above embodiments, the oil outlet n of the second safety valve 44 is connected to the oil inlet m of the variable pump body 41 of the variable pump.

[0060] Embodiment 4

[0061] As Figure 3 and Figure 4 Based on Embodiments 1-3, the oil replenishing and overflow valve group further includes an overflow valve 45 having an oil inlet m and an oil outlet n. The oil inlet m of the overflow valve 45 is connected to the oil outlet n of the gear pump 2. The oil outlet n of the overflow valve 45 is connected to the oil tank 13. The overflow valve 45, the first safety valve 43, and the second safety valve 44 are arranged in parallel.

[0062] The beneficial effect of adopting the preferred solution in the above embodiments is that in the oil replenishing standby state, when the fan 9 starts, the gear pump 2 transports the hydraulic oil to the drive pump 4 through the pipeline, and then transports the oil to the pipeline through the first safety valve 43 and the second safety valve 44 respectively. When the oil pressure rises to the required value and reaches the set value of the overflow valve 45, the overflow valve 45 opens, transports the excess oil back to the oil tank 13, maintains this pressure value, realizes replenishing the oil in the pipeline, maintains low oil pressure operation, and waits for the subsequent command of the system.

[0063] Embodiment 5

[0064] As Figure 3 andFigure 4 , on the basis of Embodiments 1-4, the drive pump control valve 5 includes a first proportional solenoid valve 51, a second proportional solenoid valve 52, a spool plunger 53, and a variable spool 54. Both the first proportional solenoid valve 51 and the second proportional solenoid valve 52 have an oil inlet m and an oil outlet n. The spool plunger 53 has a left oil chamber e and a right oil chamber f. The variable spool 54 has a left oil chamber c and a right oil chamber d. The oil outlet n of the first proportional solenoid valve 51 communicates with the left oil chamber e of the spool plunger 53. The oil outlet n of the second proportional solenoid valve 52 communicates with the right oil chamber f of the spool plunger 53. And the spool plunger 53 is connected to the variable spool 54. The variable spool 54 is also connected to the variable pump at the same time. The oil outlet n of the gear pump 2 communicates with the oil inlets m of both the first proportional solenoid valve 51 and the second proportional solenoid valve 52, and communicates with the variable pump through the right oil chamber d of the variable spool 54. And the variable pump communicates with the fuel tank 13 through the right oil chamber d of the variable spool 54.

[0065] The beneficial effect of adopting the preferred solution in the above embodiments is that when the fan 9 is in operation and during the oil pumping process, the second proportional solenoid valve 52 is energized. The gear pump 2 pumps the pressure oil in the fuel tank 13 and delivers it to the oil inlet m of the second proportional solenoid valve 52, and then delivers it to the right oil chamber f of the spool plunger 53 through the oil outlet n of the second proportional solenoid valve 52, forcing it to move the spool driving the variable spool 54. At the same time, the gear pump 2 pumps the pressure oil to the right oil chamber d of the variable spool 54, and the oil pressure is then delivered to the variable pump and continuously outputs high-pressure oil through the variable pump. At this time, the gear pump 2 pumps the pressure oil to the oil inlet m of the oil replenishing and overflow valve group. The pressure oil is pumped to the motor 8 through the oil outlet n of the oil replenishing and overflow valve group. The pressure oil is delivered to the oil inlet m of the variable pump through the oil outlet n of the oil replenishing and overflow valve group, and then is delivered to the motor 8 through the oil outlet n of the variable pump, realizing the operation of the motor 8, driving the rotation of the fan 9, generating a certain negative pressure value for seeding operations.

[0066] During the oil return process, the pressure oil returns to the oil inlet m of the variable pump housing 41 through the oil outlet n of the motor 8 to realize circulation, and the oil in the left oil chamber a of the variable plunger 42 is delivered back to the fuel tank 13 through the right oil chamber d of the variable spool 54.

[0067] Based on the above embodiments, the variable spool 54 is also connected to the variable plunger 42 and the variable pump housing 41 simultaneously. The gear pump 2 pumps the pressure oil to the right oil chamber d of the variable spool 54, and after the oil pressure is transmitted, it is sent to the variable pump (specifically, the right oil chamber b of the variable plunger 42). The plunger of the variable plunger 42 moves to change the displacement of the variable pump housing 41, and high-pressure oil is continuously output through the variable pump. At this time, the gear pump 2 pumps the pressure oil to the oil inlets m of the first safety valve 43 and the second safety valve 44. The pressure oil is pumped to the motor 8 through the oil outlet n of the first safety valve 43, and the pressure oil is sent to the oil inlet m of the variable pump housing 41 through the oil outlet n of the second safety valve 44, and then is sent to the motor 8 through the oil outlet n of the variable pump housing 41, realizing the operation of the motor 8, driving the rotation of the fan 9, generating a certain negative pressure value for seeding operations.

[0068] Among them, the variable spool 54 is also connected to the variable plunger 42 and the variable pump housing 41 through a connecting rod.

[0069] Embodiment 6

[0070] As Figure 1 and Figure 2 , based on Embodiments 1-5, both the first proportional solenoid valve 51 and the second proportional solenoid valve 52 have oil drain ports L, and both oil drain ports L communicate with the oil tank 13.

[0071] The beneficial effect of adopting the preferred scheme in the above embodiments is that when the system pressure is too high, the oil is conveyed back to the oil tank 13 through the oil drain port L to ensure smooth oil return, avoid the influence of back pressure on the system, and protect the hydraulic system from overpressure damage.

[0072] Embodiment 7

[0073] As Figure 1 and Figure 2 , based on Embodiments 1-6, the oil outlet n of the first proportional solenoid valve 51, the oil outlet n of the second proportional solenoid valve 52, and the left oil chamber e and the right oil chamber f of the spool plunger 53 all communicate with the oil tank 13.

[0074] The beneficial effect of adopting the preferred scheme in the above embodiments is that it provides an oil return path for the first proportional solenoid valve 51, the second proportional solenoid valve 52, and the spool plunger 53. By returning the excess oil to the oil tank, the system pressure can be effectively maintained stable, avoiding excessive pressure caused by oil accumulation, and avoiding back pressure during the oil return process, thereby improving the control accuracy and response speed of the system; the left oil chamber e and the right oil chamber f of the spool plunger 53 communicate with the oil tank 13, which can balance the pressure and serve as a pressure relief channel when the system pressure is too high, protecting the spool and related hydraulic components.

[0075] Embodiment 8

[0076] As Figure 5 and Figure 6 , on the basis of Embodiments 1-7, a blower drive hydraulic system of a seeder according to the present invention further includes a wind pressure sensor 10 and a controller 12 communicatively connected to the wind pressure sensor 10. The wind pressure sensor 10 is disposed on the blower 9, and the controller 12 is further connected to the drive pump control valve 5. The controller 12 includes a display module.

[0077] The beneficial effect of adopting the preferred solution in the above embodiment is that when the blower 9 is in operation, the negative pressure value generated by the rotation of the blower 9 can be monitored in real time through the wind pressure sensor 10, and the monitored value is transmitted to the controller 12. The controller 12 displays the value in real time through the display module. The operator can manually adjust the input current value of the drive pump control valve 5 according to this value. After the negative pressure value is adjusted to an appropriate value, the operation can be stopped, and the seeder can operate normally.

[0078] Among them, the display module can be a display screen.

[0079] On the basis of the above embodiment, the controller 12 is further connected to the second proportional solenoid valve 52 of the drive pump control valve 5.

[0080] Embodiment 9

[0081] As Figure 5 and Figure 6 , on the basis of Embodiments 1-8, a blower drive hydraulic system of a seeder according to the present invention further includes a rotational speed sensor 11 communicatively connected to the controller 12. The rotational speed sensor 11 is used to detect the shaft rotational speed of the motor 8 to obtain a real-time rotational speed value x, so as to adjust the current value of the drive pump control valve 5 through the controller 12 when the real-time rotational speed value x is lower than a threshold value y.

[0082] The beneficial effect of adopting the preferred solution in the above embodiment is that when the blower 9 is in operation, the shaft rotational speed of the motor 8 can be monitored in real time through the rotational speed sensor 11 to obtain a real-time rotational speed value x, and it is transmitted to the controller 12. The controller 12 compares the real-time rotational speed value x with the threshold value y. When the real-time rotational speed value x is lower than the threshold value y, the controller 12 adjusts the current value of the drive pump control valve 5, forcing the displacement of the variable pump to increase, the output flow rate to increase, the rotational speed of the motor 8 to gradually increase, the rotational speed of the blower 9 to increase, and the negative pressure value generated by the blower 9 to gradually increase until the operation requirements are met, and the input current value of the second proportional solenoid valve 52 of the drive pump control valve 5 remains unchanged.

[0083] When the input speed of the variable pump body 41 of the variable pump fluctuates or the load of the seeder changes, the input current value of the second proportional solenoid valve 52 of the drive pump control valve 5 immediately responds until the wind pressure generated by the fan 9 is adjusted to the appropriate operating range, achieving automatic adjustment. To achieve remote control, which is convenient and fast.

[0084] Based on the above embodiments, the display module includes a display lamp and / or a buzzer, so that when the real-time speed value x is lower than the threshold value y, the controller 12 gives a lighting and / or buzzer alarm through the display module.

[0085] When the real-time speed value x is lower than the threshold value y, the controller 12 adjusts the current value of the second proportional solenoid valve 52 of the drive pump control valve 5, forcing the displacement of the variable pump body 41 of the variable pump to increase.

[0086] Embodiment 10

[0087] As Figure 9 , based on Embodiments 1-9, a seeder fan drive hydraulic system according to the present invention further includes a first bypass valve 7 having an oil inlet m and an oil outlet n. The oil inlet m of the first bypass valve 7 is communicated with the oil outlet n of the motor 8, and the oil outlet n of the first bypass valve 7 is communicated with the oil inlet m of the motor 8.

[0088] The beneficial effect of adopting the preferred solution in the above embodiment is that when the drive of the fan 9 stops, the fan 9 will continue to drive the motor 8 to rotate due to its own inertia, which will generate a certain high-pressure oil at the oil outlet n position of the motor 8. The first bypass valve 7 can prevent the pressure from being too high, resulting in oil dispersion and pipeline failures. The excessive pressure oil can reach the oil inlet m of the motor 8 through the first bypass valve 7, and the motor 8 itself can generate a circulation of the oil until it stops rotating, achieving the purpose of shutdown buffering.

[0089] Embodiment 11

[0090] As Figure 5 and Figure 6 , based on Embodiments 1-10, a seeder fan drive hydraulic system according to the present invention further includes a hydraulic oil radiator 6 having an oil inlet m and an oil outlet n. The oil inlet m of the hydraulic oil radiator 6 is communicated with the oil outlet n of the motor 8, and the oil outlet n of the hydraulic oil radiator 6 is communicated with the oil inlet m of the variable pump body 41.

[0091] The beneficial effects of adopting the preferred solutions in the above embodiments are as follows. When the fan 9 is in operation, high-pressure oil reaches the motor 8 through the pipeline, and the return oil is cooled by the hydraulic oil radiator 6 and then returns to the oil inlet m of the variable pump body 41 of the variable pump to reduce the temperature of the high-pressure oil through the hydraulic oil radiator 6, effectively preventing the hydraulic oil from deteriorating or being damaged due to excessive temperature, maintaining the performance of the hydraulic oil, improving the system efficiency and reliability, preventing leakage, ensuring the normal operation of the hydraulic system, extending the service life of the equipment, and also contributing to energy conservation and environmental protection.

[0092] Based on the above embodiments, a second bypass valve 61 is connected in parallel with the hydraulic oil radiator 6. The second bypass valve 61 has an oil inlet m and an oil outlet n. The oil inlet m of the second bypass valve 61 is connected to the oil outlet n of the motor 8, and the oil outlet n is connected to the oil inlet m of the variable pump body 41 of the variable pump.

[0093] When the inside of the hydraulic oil radiator 6 is blocked, the back pressure at the oil inlet of the hydraulic oil radiator 6 will increase. When the pressure exceeds the set value (for example, 0.45 MPa), the second bypass valve 61 will open, allowing some hydraulic oil to bypass the hydraulic oil radiator 6 and directly return to the variable pump body 41 of the variable pump, thus avoiding damage to the hydraulic oil radiator 6 due to excessive pressure and ensuring the normal operation of the system.

[0094] Embodiment 12

[0095] As Figure 1 and Figure 2 , based on Embodiments 1-11, a seeder fan-driven hydraulic system according to the present invention further includes a filter 1 and a pressure filter 3 both having an oil inlet m and an oil outlet n. The oil inlet m of the filter 1 is connected to the fuel tank 13, and the oil outlet n is connected to the oil inlet m of the gear pump 2. The oil inlet m of the pressure filter 3 is connected to the oil outlet n of the gear pump 2, and the oil outlet n is simultaneously connected to the oil inlet m of the oil replenishing overflow valve group and the drive pump control valve 5.

[0096] The beneficial effects of adopting the preferred solutions in the above embodiments are as follows. The impurities and particles in the oil entering the gear pump 2 can be filtered by the filter 1 to prevent these impurities from entering the pump, thereby protecting the internal parts of the gear pump 2 and avoiding wear and blockage. And the oil pressurized by the gear pump 2 is filtered by the pressure filter 3 to further remove the impurities in the oil and ensure that the oil remains clean during transportation.

[0097] Based on the above embodiments, the oil outlet n of the pressure filter 3 is simultaneously connected to the oil inlets m of the first safety valve 43, the second safety valve 44, the first proportional solenoid valve 51, and the second proportional solenoid valve 52.

[0098] The pressure filter 3 also has an oil drain port L. The pressure filter 3 is connected to the oil tank 13 through the oil drain port L. When the pressure difference of the pressure filter 3 exceeds the set value, the oil drain port L can serve as a backup pressure relief channel to return the excess oil to the oil tank, ensuring the stability of the system pressure. The design of the oil drain port L helps to maintain the normal operation of the hydraulic system, ensuring that the oil can flow smoothly back to the oil tank and avoiding excessive pressure caused by oil accumulation.

[0099] Embodiment 13

[0100] The present invention also provides a seeder, including a seeder fan drive hydraulic system as described in Embodiments 1-12.

[0101] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus cannot be construed as a limitation of the present invention.

[0102] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one of such features. In the description of the present invention, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically defined.

[0103] In the present invention, unless otherwise clearly defined and limited, the terms "mounted", "connected", "connected", "fixed", etc. should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication of two elements or the interaction relationship between two elements, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0104] In the present invention, unless otherwise clearly defined or limited, the first feature being "on" or "under" the second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature being "under", "below" and "beneath" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply indicates that the horizontal height of the first feature is less than that of the second feature.

[0105] In the description of this specification, the descriptions with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms are not necessarily directed to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, without contradiction, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0106] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A blower driving hydraulic system for a seed drill, comprising a motor (8) having an oil inlet m and an oil outlet n and a blower (9) drivingly connected to an output shaft of the motor (8), characterized in that: It also includes an oil tank (13), a drive pump (4), a drive pump control valve (5), and a gear pump (2) having an oil inlet m and an oil outlet n. The drive pump (4) includes an oil replenishment overflow valve group and a variable pump, both of which have an oil inlet m and an oil outlet n. The oil outlet n of the gear pump (2) is simultaneously connected to the oil replenishment overflow valve group and the oil inlet m of the drive pump control valve (5). The oil outlet n of the oil replenishment overflow valve group is simultaneously connected to the variable pump, the oil inlet m of the motor (8), and the oil tank (13). The oil outlet n of the variable pump is connected to the oil inlet m of the motor (8). The oil outlet of the motor (8) is also connected to the oil inlet m of the variable pump. The drive pump control valve (5) is connected to the variable pump. The drive pump control valve (5) and the variable pump are both connected to the oil tank (13).

2. A blower driving hydraulic system for a seed drill according to claim 1, characterized in that: The variable pump comprises a variable pump body (41) having an oil inlet m and an oil outlet n, and a variable plunger (42) having a left oil chamber a and a right oil chamber b, wherein the oil inlet m of the variable pump body (41) is connected to the oil outlet n of the motor (8), the variable plunger (42) is connected to the swash plate of the variable pump body (41), the drive pump control valve (5) is connected to the variable plunger (42) and the variable pump body (41) at the same time, and the left oil chamber a of the variable plunger (42) is connected to the oil tank (13) through the drive pump control valve (5).

3. A blower driving hydraulic system for a seed drill according to claim 1, characterized in that: The oil replenishment overflow valve group comprises a first safety valve (43) and a second safety valve (44), each having an oil inlet m and an oil outlet n. The oil outlet n of the gear pump (2) is connected to the oil inlets m of the first safety valve (43) and the second safety valve (44) at the same time. The oil outlet n of the first safety valve (43) is connected to the oil inlet m of the oil tank (13) and the motor (8) at the same time. The oil outlet n of the second safety valve (44) is connected to the oil tank (13) and the oil inlet m of the variable pump at the same time.

4. A blower driving hydraulic system for a seed drill according to claim 3, characterized in that: The oil replenishment relief valve group also includes a relief valve (45) having an oil inlet m and an oil outlet n. The oil inlet m of the relief valve (45) is connected to the oil outlet n of the gear pump (2), and the oil outlet n of the relief valve (45) is connected to the oil tank (13). The relief valve (45), the first safety valve (43) and the second safety valve (44) are arranged in parallel.

5. A blower driving hydraulic system for a seed drill according to claim 1, characterized in that: The driving pump control valve (5) comprises a first proportional solenoid valve (51), a second proportional solenoid valve (52), a valve core plunger (53) and a variable valve core (54); the first proportional solenoid valve (51) and the second proportional solenoid valve (52) both have an oil inlet m and an oil outlet n; the valve core plunger (53) has a left oil chamber e and a right oil chamber f; the variable valve core (54) has a left oil chamber c and a right oil chamber d; the oil outlet n of the first proportional solenoid valve (51) is connected to the left oil chamber e of the valve core plunger (53); the second proportional solenoid valve (52) is connected to the left oil chamber e of the valve core plunger (53); The oil outlet n of (52) is connected to the right oil chamber f of the valve core plunger (53), and the valve core plunger (53) is connected to the variable valve core (54), and the variable valve core (54) is also connected to the variable pump. The oil outlet n of the gear pump (2) is connected to the oil inlet m of the first proportional solenoid valve (51) and the second proportional solenoid valve (52), and is connected to the variable pump through the right oil chamber d of the variable valve core (54), and the variable pump is connected to the oil tank (13) through the right oil chamber d of the variable valve core (54).

6. A blower driving hydraulic system for a seed drill according to claim 5, characterized in that: The first proportional solenoid valve (51) and the second proportional solenoid valve (52) both have an oil drain port L, and both of the oil drain ports L are connected to the oil tank (13).

7. A blower driving hydraulic system for a seed drill according to claim 5, characterized in that: The oil outlet n of the first proportional solenoid valve (51), the oil outlet n of the second proportional solenoid valve (52), and the left oil chamber e and the right oil chamber f of the valve core plunger (53) are all connected to the oil tank (13).

8. The blower driving hydraulic system of a seed drill according to claim 1, characterized in that: It also includes a wind pressure sensor (10) and a controller (12) communicatively connected to the wind pressure sensor (10), wherein the wind pressure sensor (10) is arranged on the fan (9), and the controller (12) is also connected to the drive pump control valve (5), and the controller (12) includes a display module.

9. A blower driving hydraulic system for a seed drill according to claim 8, characterized in that: It also includes a speed sensor (11) that is communicatively connected to the controller (12), and the speed sensor (11) is used to detect the shaft speed of the motor (8) to obtain a real-time speed value x, so that when the real-time speed value x is lower than a threshold value y, the current value of the drive pump control valve (5) is adjusted through the controller (12).

10. A blower driving hydraulic system for a seed drill according to any one of claims 1 to 9, characterized in that: It also includes a first bypass valve (7) having an oil inlet m and an oil outlet n, wherein the oil inlet m of the first bypass valve (7) is connected to the oil outlet n of the motor (8), and the oil outlet n of the first bypass valve (7) is connected to the oil inlet m of the motor (8).

11. A blower driving hydraulic system for a seed drill according to any one of claims 1 to 9, characterized in that: It also includes a hydraulic oil radiator (6) having an oil inlet m and an oil outlet n, wherein the oil inlet m of the hydraulic oil radiator (6) is connected to the oil outlet n of the motor (8), and the oil outlet n of the hydraulic oil radiator (6) is connected to the oil inlet m of the variable pump.

12. A blower driving hydraulic system for a seed drill according to any one of claims 1 to 9, characterized in that: It also includes a filter (1) and a pressure filter (3), each having an oil inlet m and an oil outlet n, wherein the oil inlet m of the filter (1) is connected to the oil tank (13), and the oil outlet n is connected to the oil inlet m of the gear pump (2); the oil inlet m of the pressure filter (3) is connected to the oil outlet n of the gear pump (2), and the oil outlet n is simultaneously connected to the oil inlet m of the oil replenishment overflow valve group and the drive pump control valve (5).

13. A seed drill, characterized in that: It comprises a seed drill fan drive hydraulic system as described in any one of claims 1-12.

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