PTO transfer case for rotary cultivator

Abstract

The utility model discloses a PTO transfer case for a rotary cultivator, which comprises a case body, a power input shaft and a PTO output shaft, one end of the power input shaft extends into the box body and then is connected with a duplex normally-open type clutch, the duplex normally-open type clutch comprises a driving shaft and two driven gears, namely a first driven gear and a second driven gear, the driving shaft is connected with the power input shaft, the first driven gear is connected with a PTO output shaft after passing through a three-stage speed reducing mechanism, and the second driven gear is connected with the PTO output shaft after passing through a three-stage speed reducing mechanism. An oil pump driving shaft is further arranged in the box body, and the second driven gear is connected with the oil pump driving shaft after passing through a two-stage transmission mechanism; and one end, close to the duplex plunger pump, of the oil pump driving shaft extends out of the box body and then is connected with a pump shaft of the duplex plunger pump. According to the utility model, PTO output and walking output are completely independent, so that control can be carried out more easily and quickly, meanwhile, the safety in the operation process can be effectively improved, and the cost is reduced.

Description

Technical Field

[0001] This utility model relates to the field of rotary tiller technology, and in particular to a PTO transfer case for rotary tillers. Background Technology

[0002] PTO transfer cases are typically used in agricultural equipment such as self-propelled tillers and rotary tillers to distribute power. After the input power passes through the PTO transfer case, it drives the PTO device and the walking device respectively, thereby driving the agricultural equipment to work.

[0003] Currently, conventional PTO transfer cases connect the power input shaft to the drive shaft via a normally closed clutch. Power is then split through the drive shaft and gears, and finally output through the PTO output shaft and travel output shaft. However, this structure has poor safety during use, especially when the machine is not stopped. To stop operation or travel, the clutch must be kept disengaged, which is not only unsafe but also extremely inconvenient for operators. Furthermore, existing PTO transfer cases can only split and transmit power, not control the travel power. Therefore, a travel speed control mechanism is required during assembly, further complicating the PTO transfer case structure, increasing operational complexity, and significantly raising the overall cost. Utility Model Content

[0004] In view of the above-mentioned shortcomings of the existing technology, the purpose of this utility model is to solve the problems of complex structure, cumbersome operation, poor safety and high cost of the existing PTO transfer case, and to provide a PTO transfer case for rotary tillers with a simpler overall structure, and completely independent PTO output and travel output, so as to make control easier and faster, while effectively improving safety during operation and reducing costs.

[0005] To solve the above-mentioned technical problems, the technical solution adopted by this utility model is as follows: a PTO transfer case for a rotary tiller, comprising a case body, a power input shaft, and a PTO output shaft, wherein the power input shaft and the PTO output shaft are located on opposite sides of the case body; characterized in that: one end of the power input shaft extends into the case body and is connected to a double normally open hydraulic clutch, the double normally open hydraulic clutch comprising a drive shaft and two driven gears: a first driven gear and a second driven gear, the drive shaft being connected to the power input shaft and capable of rotating synchronously with the power input shaft; the first driven gear being connected to the PTO output shaft after a three-stage reduction mechanism and capable of driving the PTO output shaft to rotate; an oil pump drive shaft is also provided inside the case body, the second driven gear being connected to the oil pump drive shaft after a two-stage transmission mechanism and capable of driving the oil pump drive shaft to rotate;

[0006] It also includes a double plunger pump, which is located on the same side of the housing as the power input shaft and is fixedly connected to the housing. The end of the oil pump drive shaft near the double plunger pump extends out of the housing and is connected to the pump shaft of the double plunger pump.

[0007] Furthermore, the dual normally open clutch is a hydraulic clutch.

[0008] Further, the double-drive normally open clutch includes a drive shaft, a first driven gear, a second driven gear, a drive housing, a drive friction disc, a driven friction disc, and a compression disc; the drive housing is a tubular structure and is sleeved on the drive shaft, with its middle part fixedly connected to the drive shaft via a connecting disc; a compression disc is sleeved on both sides of the connecting disc, with a gap between the compression disc and the connecting disc, and its inner and outer sides respectively having clearance fit with the drive shaft and the drive housing; the first driven gear and the second driven gear are both double gears, located at both ends of the drive housing respectively, and rotatably connected to the drive shaft; the first driven gear... One of the second driven gears extends into the driving housing; several driving friction discs and driven friction discs are distributed between both ends of the housing and the gear extending into the housing, and the driving and driven friction discs are alternately distributed and clearance-fitted; several slots are provided around the driving housing near both ends, and the slots penetrate both ends of the driving housing; the driving friction discs have lugs corresponding to the slots, and the lugs extend into the corresponding slots; the driven friction discs have toothed holes on their inner sides, and are fitted onto the gears through the toothed holes to form meshing; a limiting retaining ring is provided at each of the two ends of the inner side of the driving housing;

[0009] One end of the drive shaft is connected to the power input shaft, and the other end is provided with two oil inlet channels and one oil return channel along the axial direction. The two oil inlet channels are connected to the gap between the two extrusion plates and the connecting plate, and the oil return channel is connected to the gap between the two extrusion plates and the connecting plate. The end of the drive shaft away from the power input shaft extends out of the housing and is connected to a valve seat. The valve seat has an oil inlet hole and an oil return hole, and the oil inlet hole is connected to the oil inlet channel, and the oil return hole is connected to the oil return channel.

[0010] Furthermore, sealing rings are provided between the inner side of the extrusion disc and the drive shaft, and between the outer side of the extrusion disc and the drive housing.

[0011] Furthermore, on the drive shaft, grooves are provided around the drive shaft at the positions corresponding to the oil inlet and oil return holes, and sealing rings are provided on both sides of the two grooves.

[0012] Furthermore, there is a gap between the first driven gear and the inner side of the gear extending into the drive housing and the drive shaft. A spring pressure plate is provided in the gap and the spring pressure plate is sleeved on the drive shaft. A separation spring is provided between the spring pressure plate and the extrusion plate. The separation spring is sleeved on the drive shaft and its two ends are in close contact with the spring pressure plate and the extrusion plate, respectively.

[0013] Furthermore, a limiting retaining ring is provided on the side of the spring pressure plate away from the extrusion plate. On the drive shaft, a groove is provided at the position corresponding to the limiting retaining ring. The limiting retaining ring is engaged in the groove, and its outer edge protrudes out of the drive shaft.

[0014] Furthermore, the three-stage reduction mechanism includes a first transmission shaft and a second transmission shaft. The first transmission shaft is provided with a first reduction drive gear and a first reduction driven gear, wherein the first reduction drive gear meshes with the first driven gear. The second transmission shaft is provided with a second reduction drive gear and a second reduction driven gear, wherein the second reduction drive gear meshes with the first reduction driven gear. A PTO output gear is provided on the PTO output shaft, and the PTO output gear meshes with the second reduction driven gear.

[0015] Furthermore, the two-stage transmission mechanism includes a third transmission shaft and a fourth transmission shaft. The third transmission shaft is provided with a transition gear, which meshes with a second driven gear. The fourth transmission shaft is provided with a third reduction drive gear and a third reduction driven gear, which meshes with the transition gear. The oil pump drive shaft is provided with a travel output gear, which meshes with the third reduction driven gear.

[0016] Compared with the prior art, the present invention has the following advantages:

[0017] 1. The overall structure is simpler, and the PTO output and travel output can be completely independently controlled, which greatly improves the safety of the rotary tiller during operation; at the same time, the oil pump drive shaft drives the double plunger pump to rotate, and the double plunger pump drives the hydraulic travel motors on both sides to achieve travel output, which makes control easier and faster.

[0018] 2. Since this solution uses hydraulic control for clutch engagement and disengagement, only the addition of solenoid valves, wireless control devices, etc., is needed to achieve remote electronic clutch operation, thereby facilitating remote control and unmanned driving, and providing greater scalability. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the structure of this utility model.

[0020] Figure 2 This is a schematic diagram of the structure of this utility model after part of the outer shell has been removed.

[0021] Figure 3 This is a structural diagram of the present invention from another angle after part of the outer shell has been removed.

[0022] Figure 4 This is a side view of the present invention after removing part of the outer shell and valve seat.

[0023] Figure 5 For this Figure 4 A sectional view along line A-A.

[0024] In the diagram: 1—box body, 2—power input shaft, 3—PTO output shaft, 4—clutch, 41—drive shaft, 42—first driven gear, 43—second driven gear, 44—drive housing, 45—drive friction disc, 46—driven friction disc, 47—extrusion disc, 48—connecting disc, 49—oil inlet channel, 410—oil return channel, 5—oil pump drive shaft, 6—double plunger pump, 7—valve seat, 8—first drive shaft, 9—second drive shaft, 10—first reduction drive gear, 11—first reduction driven gear, 12—second reduction drive gear, 13—second reduction driven gear, 14—PTO output gear, 15—third drive shaft, 16—fourth drive shaft, 17—transition gear, 18—third reduction drive gear, 19—third reduction driven gear, 20—travel output gear. Detailed Implementation

[0025] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0026] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this utility model, not all of them. Therefore, the following detailed description of the embodiments of this utility model provided in the accompanying drawings is not intended to limit the scope of the claimed utility model, but merely to represent selected embodiments of this utility model. All other embodiments obtained by those skilled in the art based on the embodiments of this utility model without inventive effort are within the scope of protection of this utility model.

[0027] It should be noted that similar reference numerals and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures. In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the figures, or the orientation or positional relationship commonly used when the product is in use. They are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first," "second," and "third," etc., are only used to distinguish descriptions and should not be construed as indicating or implying relative importance. In addition, the terms "horizontal," "vertical," etc., do not indicate that the component is required to be absolutely horizontal or suspended, but can be slightly tilted. For example, "horizontal" simply means that its direction is more horizontal than "vertical," and does not mean that the structure must be completely horizontal, but can be slightly tilted. In the description of this invention, it should also be noted that, unless otherwise explicitly specified and limited, the terms "set," "install," "connect," and "link" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0028] Example: See Figures 1 to 5 A PTO transfer case for a rotary tiller includes a housing 1, a power input shaft 2, and a PTO output shaft 3, wherein the power input shaft 2 and the PTO output shaft 3 are located on opposite sides of the housing 1. One end of the power input shaft 2 extends into the housing 1 and is connected to a double normally open clutch 4. The double normally open clutch 4 includes a drive shaft 41 and two driven gears: a first driven gear 42 and a second driven gear 43. The drive shaft 41 is connected to the power input shaft 2 and can rotate synchronously with the power input shaft 2. The double normally open clutch 4 is a hydraulic clutch.

[0029] Specifically, the double-drive normally open clutch 4 includes a drive shaft 41, a first driven gear 42, a second driven gear 43, a drive housing 44, a drive friction disc 45, a driven friction disc 46, and a pressure disc 47. The drive housing 44 is a tubular structure and is fitted onto the drive shaft 41, with its central portion fixedly connected to the drive shaft 41 via a connecting disc 48. A pressure disc 47 is fitted onto each side of the connecting disc 48, with a gap between the pressure disc 47 and the connecting disc 48, and its inner and outer sides respectively having clearance fits with the drive shaft 41 and the drive housing 44. In implementation, sealing rings are provided between the inner side of the pressure disc 47 and the drive shaft 41, and between the outer side of the pressure disc 47 and the drive housing 44, and the pressure disc 47 is always in contact with the two sealing rings during movement, thereby preventing oil leakage. The first driven gear 42 and the second driven gear 43 are both double gears, located at opposite ends of the drive housing 44, and rotatably connected to the drive shaft 41. One of the first driven gear 42 and the second driven gear 43 extends into the driving housing 44. In practice, bushings are provided between the gears of the first driven gear 42 and the second driven gear 43 located outside the driving housing 44 and the driving shaft 41. Several driving friction discs 45 and driven friction discs 46 are distributed between the two ends of the housing and the gears extending into the housing, and the driving friction discs 45 and driven friction discs 46 are alternately distributed and clearance-fitted. Among them, several slots are provided around the driving housing 44 near both ends, and the slots penetrate both ends of the driving housing 44 (i.e., the slots penetrate one adjacent end of the driving housing 44). The driving friction discs 45 have lugs corresponding to the slots, and the lugs extend into the corresponding slots. The driven friction discs 46 have toothed holes on their inner sides, and are fitted onto the gears through the toothed holes to form meshing. A limiting ring is provided at each end of the inner side of the active housing 44 to limit the active friction disk 45 and the driven friction disk 46, thereby pressing the active friction disk 45 and the driven friction disk 46 together, so as to generate friction between the active friction disk 45 and the driven friction disk 46 and realize power transmission.

[0030] One end of the drive shaft 41 is connected to the power input shaft 2, and the other end has two oil inlet channels 49 and one oil return channel 410 along the axial direction. The two oil inlet channels 49 are connected to the gaps between the two extrusion discs 47 and the connecting disc 48, and the oil return channel 410 is also connected to the gaps between the two extrusion discs 47 and the connecting disc 48. The end of the drive shaft 41 away from the power input shaft 2 extends out of the housing 1 and is connected to a valve seat 7. The valve seat 7 has an oil inlet hole and an oil return hole, with the oil inlet hole connected to the oil inlet channel 49 and the oil return hole connected to the oil return channel 410. On the drive shaft 41, grooves are provided around the drive shaft 41 at the positions corresponding to the oil inlet hole and the oil return hole, and sealing rings are provided on both sides of the grooves. In actual machining, the valve seat 7 has one oil inlet hole, which is simultaneously connected to two oil inlet channels 49. As an optimization, the oil inlet channels 49 and the oil inlet hole are located on the same circumference coaxial with the drive shaft 41, which makes machining and operation more convenient. As another implementation, the valve seat 7 has two oil inlets, which are respectively connected to two oil inlet channels 49, thus enabling more effective independent control of power output.

[0031] In specific implementation, the inner diameters of the first driven gear 42 and the second driven gear 43 extending into the drive housing 44 are larger than the diameter of the drive shaft 41, creating a gap between the inner sides of the first driven gear 42 and the second driven gear 43 extending into the drive housing 44 and the drive shaft 41. A spring pressure plate is installed in this gap, and the spring pressure plate is sleeved on the drive shaft 41. A separation spring (not shown in the figure) is installed between the spring pressure plate and the pressure plate 47, and the separation spring is sleeved on the drive shaft 41, with its two ends tightly against the spring pressure plate and the pressure plate 47, respectively. This allows for rapid separation during clutch disengagement. A limiting retaining ring is provided on the side of the spring pressure plate away from the pressure plate 47, and a groove is provided on the drive shaft 41 corresponding to the position of the limiting retaining ring. The limiting retaining ring is engaged in this groove, and its outer edge protrudes from the drive shaft 41, thereby ensuring the stability of the spring operation.

[0032] The first driven gear 42 is connected to the PTO output shaft 3 via a three-stage reduction mechanism and can drive the PTO output shaft 3 to rotate. The three-stage reduction mechanism includes a first drive shaft 8 and a second drive shaft 9. The first drive shaft 8 has a first reduction drive gear 10 and a first reduction driven gear 11, wherein the first reduction drive gear 10 meshes with the first driven gear 42. The second drive shaft 9 has a second reduction drive gear 12 and a second reduction driven gear 13, wherein the second reduction drive gear 12 meshes with the first reduction driven gear 11. The PTO output shaft 3 has a PTO output gear 14 (reduction output gear), which meshes with the second reduction driven gear 13.

[0033] An oil pump drive shaft 5 is also provided inside the housing 1. The second driven gear 43 is connected to the oil pump drive shaft 5 via a two-stage transmission mechanism and can drive the oil pump drive shaft 5 to rotate. The two-stage transmission mechanism includes a third transmission shaft 15 and a fourth transmission shaft 16. A transition gear 17 is provided on the third transmission shaft 15, and the transition gear 17 meshes with the second driven gear 43. A third reduction drive gear 18 and a third reduction driven gear 19 are provided on the fourth transmission shaft 16, and the third reduction drive gear 18 meshes with the transition gear 17. A travel output gear 20 is provided on the oil pump drive shaft 5, and the travel output gear 20 meshes with the third reduction driven gear 19.

[0034] It also includes a double plunger pump 6, which is located on the same side of the housing 1 as the power input shaft 2 and is fixedly connected to the housing 1. The end of the oil pump drive shaft 5 near the double plunger pump 6 extends out of the housing 1 and is connected to the pump shaft of the double plunger pump 6.

[0035] During operation, this solution only requires connecting an external oil pump, oil tank, and solenoid valve to the valve seat 7, and then supplying oil to the gap between the extrusion plate 47 and the connecting plate 48 as needed, thereby pushing the extrusion plate 47 to move. This enables the clutch to engage and transmit power. Operation is simple and convenient. Furthermore, achieving independent transmission of PTO and travel through a single clutch effectively improves power transmission efficiency, enhances stability during operation, and improves the safety of the rotary tiller. Simultaneously, the oil pump drive shaft 5 drives the double plunger pump 6 to rotate, which in turn drives the hydraulic travel motors on both sides to achieve travel output, allowing for easier and faster control.

[0036] Furthermore, since this solution uses hydraulic control for clutch engagement and disengagement, only the addition of solenoid valves, wireless control devices, etc., is needed to achieve remote electronic clutch operation, thereby facilitating remote control and unmanned driving, and offering greater scalability.

[0037] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model and not to limit the technical solutions. Those skilled in the art should understand that any modifications or equivalent substitutions to the technical solutions of this utility model that do not depart from the spirit and scope of this technical solution should be covered within the scope of the claims of this utility model.

Claims

1. A PTO transfer case for a rotary tiller, comprising a housing, a power input shaft, and a PTO output shaft, wherein, The power input shaft and the PTO output shaft are located on opposite sides of the housing. The power input shaft, with one end extending into the housing, is connected to a double-locked normally open hydraulic clutch. This clutch includes a drive shaft and two driven gears: a first driven gear and a second driven gear. The drive shaft is connected to the power input shaft and rotates synchronously with it. The first driven gear is connected to the PTO output shaft via a three-stage reduction mechanism and can drive the PTO output shaft to rotate. An oil pump drive shaft is also provided within the housing. The second driven gear is connected to the oil pump drive shaft via a two-stage transmission mechanism and can drive the oil pump drive shaft to rotate. It also includes a double plunger pump, which is located on the same side of the housing as the power input shaft and is fixedly connected to the housing. The end of the oil pump drive shaft near the double plunger pump extends out of the housing and is connected to the pump shaft of the double plunger pump.

2. The PTO transfer case for a rotary tiller according to claim 1, characterized in that: The dual normally open clutch is a hydraulic clutch.

3. The PTO transfer case for a rotary tiller according to claim 2, characterized in that: The dual-drive normally open clutch includes a drive shaft, a first driven gear, a second driven gear, a drive housing, a drive friction disc, a driven friction disc, and a compression disc. The drive housing is a tubular structure and is fitted onto the drive shaft, with its central portion fixedly connected to the drive shaft via a connecting disc. A compression disc is fitted onto each side of the connecting disc, with a gap between the compression disc and the connecting disc, and its inner and outer sides respectively engaging with the drive shaft and the drive housing. The first and second driven gears are both double gears, located at opposite ends of the drive housing and rotatably connected to the drive shaft. One of the driven gears extends into the driving housing. Several driving and driven friction discs are distributed between the two ends of the housing and the gear extending into the housing, with the driving and driven friction discs alternating and in clearance fit. Several slots are provided around the driving housing near both ends, penetrating both ends of the driving housing. The driving friction discs have lugs corresponding to the slots, extending out of the corresponding slots. The driven friction discs have toothed holes on their inner sides, and are fitted onto the gears through these holes to form a meshing action. A limiting retaining ring is provided at each of the two ends of the inner side of the driving housing. One end of the drive shaft is connected to the power input shaft, and the other end is provided with two oil inlet channels and one oil return channel along the axial direction. The two oil inlet channels are connected to the gap between the two extrusion plates and the connecting plate, and the oil return channel is connected to the gap between the two extrusion plates and the connecting plate. The end of the drive shaft away from the power input shaft extends out of the housing and is connected to a valve seat. The valve seat has an oil inlet hole and an oil return hole, and the oil inlet hole is connected to the oil inlet channel, and the oil return hole is connected to the oil return channel.

4. The PTO transfer case for a rotary tiller according to claim 3, characterized in that: A sealing ring is provided between the inner side of the extrusion disc and the drive shaft, and between the outer side of the extrusion disc and the drive housing.

5. The PTO transfer case for a rotary tiller according to claim 3, characterized in that: On the drive shaft, grooves are provided around the drive shaft at the positions corresponding to the oil inlet and oil return holes, and sealing rings are provided on both sides of the two grooves.

6. The PTO transfer case for a rotary tiller according to claim 3, characterized in that: The first driven gear and the second driven gear have a gap between the gear inside the active housing and the active shaft. A spring pressure plate is provided in the gap and is sleeved on the active shaft. A separation spring is provided between the spring pressure plate and the extrusion plate. The separation spring is sleeved on the active shaft and its two ends are in close contact with the spring pressure plate and the extrusion plate, respectively.

7. The PTO transfer case for a rotary tiller according to claim 6, characterized in that: A limiting ring is provided on the side of the spring pressure plate away from the extrusion plate. On the drive shaft, a groove is provided at the position corresponding to the limiting ring. The limiting ring is locked in the groove, and its outer edge protrudes out of the drive shaft.

8. The PTO transfer case for a rotary tiller according to claim 1, characterized in that: The three-stage reduction mechanism includes a first drive shaft and a second drive shaft. The first drive shaft is provided with a first reduction drive gear and a first reduction driven gear, wherein the first reduction drive gear meshes with the first driven gear. The second drive shaft is provided with a second reduction drive gear and a second reduction driven gear, wherein the second reduction drive gear meshes with the first reduction driven gear. A PTO output gear is provided on the PTO output shaft, and the PTO output gear meshes with the second reduction driven gear.

9. The PTO transfer case for a rotary tiller according to claim 1, characterized in that: The two-stage transmission mechanism includes a third transmission shaft and a fourth transmission shaft. The third transmission shaft is provided with a transition gear, which meshes with a second driven gear. The fourth transmission shaft is provided with a third reduction drive gear and a third reduction driven gear, which meshes with the transition gear. The oil pump drive shaft is provided with a travel output gear, which meshes with the third reduction driven gear.

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