CN107781364B - Power transmission mechanism of gearbox of mini-tiller - Google Patents
Power transmission mechanism of gearbox of mini-tiller Download PDFInfo
- Publication number
- CN107781364B CN107781364B CN201711217319.XA CN201711217319A CN107781364B CN 107781364 B CN107781364 B CN 107781364B CN 201711217319 A CN201711217319 A CN 201711217319A CN 107781364 B CN107781364 B CN 107781364B
- Authority
- CN
- China
- Prior art keywords
- gear
- duplex
- main shaft
- shaft
- driving
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 48
- 230000007246 mechanism Effects 0.000 title claims abstract description 27
- 230000007935 neutral effect Effects 0.000 claims description 31
- 230000009467 reduction Effects 0.000 claims description 9
- 230000004323 axial length Effects 0.000 claims description 4
- 244000025254 Cannabis sativa Species 0.000 description 5
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 238000007792 addition Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000003971 tillage Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing orbital gears
-
- A—HUMAN NECESSITIES
- A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
- A01B—SOIL WORKING IN AGRICULTURE OR FORESTRY; PARTS, DETAILS, OR ACCESSORIES OF AGRICULTURAL MACHINES OR IMPLEMENTS, IN GENERAL
- A01B33/00—Tilling implements with rotary driven tools, e.g. in combination with fertiliser distributors or seeders, with grubbing chains, with sloping axles, with driven discs
- A01B33/08—Tools; Details, e.g. adaptations of transmissions or gearings
- A01B33/082—Transmissions; Gearings; Power distribution
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/32—Gear shift yokes, e.g. shift forks
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Power Engineering (AREA)
- Soil Sciences (AREA)
- Environmental Sciences (AREA)
- Structure Of Transmissions (AREA)
- Soil Working Implements (AREA)
Abstract
The power transmission mechanism of the mini-tiller gearbox comprises a first main shaft and a second main shaft which are positioned on the same axis, wherein the first main shaft is connected with a sun gear, the sun gear is meshed with a planetary gear, the planetary gear is meshed with an inner gear ring, the second main shaft penetrates through a planetary carrier to be supported in a shaft hole of the sun gear, the other end of the second main shaft is supported on a box body, an engaging tooth sleeve and a duplex driving gear are in spline fit on the second main shaft, and the engaging tooth sleeve can be meshed with engaging inner teeth of the sun gear or the planetary carrier; a double driven gear is fixed on the auxiliary shaft, a first driving tooth of the double driving gear can be meshed with a first driven tooth of the double driven gear, or a second driving tooth of the double driving gear can be meshed with a second driven tooth of the double driven gear, or the double driving gear can be separated from the double driven gear; a duplex reverse gear is sleeved above a reverse gear shaft, one gear of the duplex reverse gear can be meshed with the second driving gear of the duplex driving gear, and the other gear is meshed with the second driven gear of the duplex driven gear. The mechanism can output various rotating speeds.
Description
Technical Field
The invention relates to a gearbox of a mini-tiller, in particular to a power transmission mechanism of the gearbox of the mini-tiller.
Background
At present, mini-tiller is becoming increasingly popular as a device capable of reducing labor intensity of farmers. The power of the mini-tiller is transmitted through the rotation of an engine crankshaft, the torque is transmitted, the two-gear conversion is carried out through a gearbox, the quick gear or the slow gear rotating speed is realized, the torque is output by a countershaft, and the power is downwards transmitted to a travelling system or a tiller through a transmission shaft perpendicular to the countershaft, so that the mini-tiller can travel or plough.
The existing power transmission mechanism of the mini-tiller gearbox is generally provided with only one main shaft and one auxiliary shaft, the main shaft and the auxiliary shaft are connected with a crankshaft of an engine through a clutch through two-gear pairs to carry out two-gear speed change output power, the structure enables the rotating speed of the main shaft to be very high, even if the speed of the main shaft is reduced through a reduction gear pair to output a slow-gear rotating speed, the speed of the slow-gear rotating speed is still relatively high, an operator cannot keep up with the speed of a travelling device, the operation and control of the operator are very laborious, the physical power consumption is very high, and the mini-tiller is not convenient to operate by the operator.
In addition, with the development of agricultural equipment, it is desirable to use the engine of the mini-tiller as a power source to drive some additional equipment, such as a water pump, a grass mower, a grass cutter, a furrow opener, a spraying device and the like, to drive the additional equipment to work by connecting the main shaft or the auxiliary shaft of a gearbox of the mini-tiller through a coupling. However, the gearbox body has only two rotating speeds of a fast gear or a slow gear, and the two rotating speeds are relatively high, so that the additional machines such as a lawnmower, a grass cutter, a furrow opener and the like which are driven to move and walk can also walk relatively fast, an operator is difficult to adapt to keep up with the fast speeds, the additional machines such as the lawnmower, the grass cutter, the furrow opener and the like cannot be matched with the mini-tiller, and only a power device with the additional machines can be adopted, so that the selling price of the additional machines is increased, the volume and the weight of the additional machines are increased, and a plurality of inconveniences are brought to a user. Moreover, as the mini-tiller generally has only two speeds, the working speeds required by different additional machines are different, the two speeds are difficult to meet the working requirements of the different additional machines, and the application range is narrow. Therefore, the gearbox of the mini-tiller in the prior art adopts a structure with a single main shaft, is not applicable to a plurality of additional machines and tools, and cannot meet the demands of markets and users.
Disclosure of Invention
The invention aims to provide a power transmission mechanism of a mini-tiller gearbox, which has a plurality of output ends, can drive additional tools through a second main shaft or a countershaft, can realize more speed-blocking requirements and meets the requirements of driving a plurality of additional tools by using mini-tiller power, aiming at the defects that the existing mini-tiller gearbox usually has only a single main shaft, and the main shaft directly outputs power at too high rotating speed and cannot be used for directly driving the additional tools.
The technology of the invention is realized as follows: the utility model provides a mini-tiller gearbox power transmission mechanism, includes main shaft, countershaft, the main shaft includes first main shaft and the second main shaft that is located same axial lead, first main shaft is supported in the box through the bearing, a sun gear of one end circumference fixed connection of first main shaft, the sun gear is equipped with external tooth and joint internal tooth, the external tooth of sun gear meshes with the planetary gear that supports on the planet carrier, the planetary gear meshes with the ring gear that is fixed in the box, second main shaft one end passes the centre bore that the planet carrier was equipped with and supports in the shaft hole of sun gear through the bearing, the other end passes the bearing and supports in the box and be equipped with external additional machines, the spline fit has joint tooth cover and duplex driving gear on the second main shaft, joint tooth cover is stirred by first shift fork, can with the joint internal tooth meshing transmission different moment of torsion that joint internal tooth or planet carrier were equipped with; the auxiliary shaft is supported on the box body through a bearing and is parallel to the second main shaft, one end of the auxiliary shaft is provided with a bevel gear, the other end of the auxiliary shaft is provided with an external additional machine tool, the auxiliary shaft is fixedly connected with a duplex driven gear, the duplex driving gear is shifted by a second shifting fork, so that a first driving tooth of the duplex driving gear is meshed with a first driven tooth of the duplex driven gear, or a second driving tooth of the duplex driving gear is meshed with a second driven tooth of the duplex driven gear, different torques are transmitted, or the duplex driving gear is disengaged from the duplex driven gear; a reverse gear shaft is supported on the box body and is parallel to the second main shaft, a duplex reverse gear is sleeved on the reverse gear shaft in an empty mode, and the duplex reverse gear is shifted by a third shifting fork, so that one gear of the duplex reverse gear can be meshed with a second driving tooth of the duplex driving gear, and the other gear is meshed with a second driven tooth of the duplex driven gear to transmit reverse gear torque.
The sun gear is provided with an axially extending hollow shaft, one section of the shaft hole of the hollow shaft is circumferentially fixed with the first main shaft, and the other section of the shaft hole of the hollow shaft is matched with the second main shaft through a bearing.
The first driving gear of the duplex driving gear and the first driven gear of the duplex driven gear are in one speed reduction transmission ratio, and the second driving gear of the duplex driving gear and the second driven gear of the duplex driven gear are in another speed reduction transmission ratio.
A second shifting fork clamping groove is formed between the first driving tooth and the second driving tooth of the duplex driving gear.
And a neutral gear distance which is larger than the axial length of the duplex driving gear is reserved between the first driven gear and the second driven gear of the duplex driven gear, and when the duplex driving gear corresponds to the neutral gear distance, the duplex driving gear does not transmit torque to the duplex driven gear.
One end of the duplex reverse gear is provided with a third shifting fork clamping groove, the other end of the duplex reverse gear is provided with a first gear and a second gear, the first gear is used for being meshed with a second driving tooth of the duplex driving gear, and the second gear is used for being meshed with a second driven tooth of the duplex driven gear.
And one end of the joint tooth sleeve is provided with a first shifting fork clamping groove, and the other end of the joint tooth sleeve is provided with joint external teeth which can be meshed with the joint internal teeth of the planet carrier or the sun gear.
And a neutral gear space is reserved between the joint internal teeth of the planet carrier and the joint internal teeth of the sun gear, and when the joint external teeth of the joint gear sleeve correspond to the neutral gear space reserved between the joint internal teeth of the planet carrier and the sun gear, the joint gear sleeve is in the neutral gear.
The planet carrier is provided with a plurality of planet gear supporting shafts extending in the same direction, the central hole of the planet carrier is divided into an inner tooth hole section and a yielding hole section, and the yielding hole section is close to one end of the planet gear supporting shaft.
The first main shaft is connected with an output shaft of a power source of the mini-tiller through a clutch, and one ends of the second main shaft and the auxiliary shaft, which are externally connected with additional machines, are provided with splines or connecting flanges.
By adopting the scheme, the main shafts are arranged into the first main shaft and the second main shaft, the two main shafts are positioned on the same axial lead, one end of the first main shaft is fixedly connected with a sun gear in the circumferential direction, the sun gear is provided with external teeth and joint internal teeth, the external teeth of the sun gear are in constant engagement with the planetary gears supported on the planet carrier, and the planetary gears are in constant engagement with the inner gear ring fixed on the box body. One end of the second main shaft passes through a central hole arranged on the planet carrier and is supported in the shaft hole of the sun gear through a bearing, and the other end of the second main shaft is supported in the box body through a bearing and is provided with an external additional machine tool. The second main shaft is provided with an axially movable joint gear sleeve in a spline fit mode, the joint gear sleeve is shifted by the first shifting fork and can be meshed with joint internal teeth of the sun gear or the planet carrier, different torques can be transmitted between the first main shaft and the second main shaft through gear shifting, and the second main shaft can directly transmit proper rotating speeds to an additional machine tool so as to meet the requirement of utilizing micro-cultivator power to drive the additional machine tool. The second main shaft is also in spline fit with a duplex driving gear capable of axially moving. The auxiliary shaft is parallel to the second main shaft, one end of the auxiliary shaft is provided with a bevel gear, and power is transmitted to a transmission shaft of the mini-tiller walking system through the bevel gear to drive the mini-tiller to walk or cultivate; the other end of the auxiliary shaft is provided with an external additional machine tool. The auxiliary shaft is fixedly connected with a duplex driven gear, the duplex driving gear is shifted by a second shifting fork, the first driving gear of the duplex driving gear is meshed with the first driven gear of the duplex driven gear to transmit one rotating speed, or the second driving gear of the duplex driving gear is meshed with the second driven gear of the duplex driven gear to transmit the other rotating speed, and the auxiliary shaft can transmit the rotating speeds suitable for different additional tools to the additional tools through the gear change between the duplex driving gear and the duplex driven gear so as to meet the requirements of driving different additional tools by using mini-tiller power; or the duplex driving gear and the duplex driven gear are completely disengaged, so that neutral gear movement is realized, and the duplex driving gear is interrupted to directly transmit power to the duplex driven gear. A reverse gear shaft is parallel to the second main shaft, a duplex reverse gear is sleeved on the reverse gear shaft in an empty mode, and is shifted by a third shifting fork, so that one gear of the duplex reverse gear can be meshed with a second driving gear of the duplex driving gear, the other gear is meshed with a second driven gear of the duplex driven gear, reverse gear torque is transmitted, the mini-tiller is convenient to advance and retreat, and the mini-tiller can be used for large-sized cultivated lands in plain areas and small-sized cultivated lands in hills and mountains. The structure enables the power transmission mechanism of the mini-tiller gearbox to be provided with a plurality of power output ends, not only can the second main shaft be used for directly driving additional tools, but also the auxiliary shaft can be used for driving travelling wheels or tilling blades and the additional tools, and various rotating speeds can be output through gear shifting, so that the requirements of driving various additional tools by utilizing mini-tiller power can be met, and the application range of the mini-tiller is wider.
The sun gear is provided with an axially extending hollow shaft, one section of the shaft hole of the hollow shaft is circumferentially fixed with the first main shaft, and the other section of the shaft hole of the hollow shaft is matched with the second main shaft through a bearing. The structure ensures that the sun gear can be fixedly connected with the circumference of the first main shaft to transfer torque, the sun gear can support the second main shaft, the second main shaft and the first main shaft are positioned on the same axial lead, the sun gear and the second main shaft can form relative movement, and the assembly connection of the transmission mechanism is simple and convenient.
The first driving gear of the duplex driving gear and the first driven gear of the duplex driven gear are in one speed reduction transmission ratio, and the second driving gear of the duplex driving gear and the second driven gear of the duplex driven gear are in another speed reduction transmission ratio. By adopting the structure, through gear shifting conversion, torque transmission with different transmission ratios can be realized between one deceleration driving duplex gear and one deceleration driven duplex gear, the number of gears required for transmitting different transmission ratios is reduced, the complex structure of gear arrangement is simplified, the arrangement space of a transmission mechanism is reduced, and the structure of the mini-tiller gearbox is more optimized and reasonable.
A second shifting fork clamping groove is formed between the first driving tooth and the second driving tooth of the duplex driving gear. And a neutral gear distance which is larger than the axial length of the duplex driving gear is reserved between the first driven gear and the second driven gear of the duplex driven gear, and when the duplex driving gear corresponds to the neutral gear distance, the duplex driving gear does not transmit torque to the duplex driven gear. In such a combined structure, the duplex driving gear moves leftwards, the first driving gear is meshed with the first driven gear of the duplex driven gear to transfer the rotating speed of one transmission ratio, the duplex driving gear moves rightwards, the second driving gear is meshed with the second driven gear of the duplex driven gear to transfer the rotating speed of the other transmission ratio, and when the duplex driving gear corresponds to the neutral gear spacing of the duplex driven gear, the duplex driving gear is completely disengaged from the duplex driven gear to interrupt power transfer. Therefore, the duplex driving gear and the duplex driven gear can transmit different rotating speeds through gear shift, and power transmission can be interrupted, so that multiple choices are provided for users.
One end of the duplex reverse gear is provided with a third shifting fork clamping groove, the other end of the duplex reverse gear is provided with a first gear and a second gear, the first gear is used for being meshed with a second driving tooth of the duplex driving gear, and the second gear is used for being meshed with a second driven tooth of the duplex driven gear. Therefore, by moving the reverse gear duplex gear, the first gear of the duplex reverse gear is meshed with the second driving gear of the duplex driving gear on the second main shaft, the second gear of the duplex reverse gear is meshed with the second driven gear of the duplex driven gear arranged on the auxiliary shaft, and the second main shaft transmits reverse gear power to the auxiliary shaft; or the duplex reverse gear is moved to be disengaged from the duplex driving gear and the duplex driven gear, and the transmission of reverse power is interrupted. Thereby providing a variety of options for user use.
And one end of the joint tooth sleeve is provided with a first shifting fork clamping groove, and the other end of the joint tooth sleeve is provided with joint external teeth which can be meshed with the joint internal teeth of the planet carrier or the sun gear. Or, a neutral space is left between the engaging internal teeth of the planet carrier and the engaging internal teeth of the sun gear, and when the engaging external teeth of the engaging sleeve correspond to the neutral space left between the engaging internal teeth of the planet carrier and the sun gear, the engaging sleeve is in the neutral position. In this way, by moving the engaging sleeve, one rotation speed is transmitted by meshing the external teeth of the engaging sleeve with the engaging internal teeth of the sun gear, or another rotation speed is transmitted by meshing the external teeth of the engaging sleeve with the engaging internal teeth of the carrier, or the external teeth of the engaging sleeve are in the neutral position, the power transmission of the first main shaft to the second main shaft is interrupted. Thereby providing a variety of options for user use.
The planet carrier is provided with a plurality of planet gear supporting shafts extending in the same direction, the central hole of the planet carrier is divided into an inner tooth hole section and a yielding hole section, and the yielding hole section is close to one end of the planet gear supporting shaft. The structure ensures that the yielding hole section of the planet carrier can provide a neutral gear position space for the external teeth of the joint gear sleeve, so that the structure of the power transmission mechanism is more compact.
The power transmission mechanism of the mini-tiller gearbox has the advantages that the structure is simple, ingenious and compact, the multi-rotation-speed multi-gear function is realized in a small volume, a plurality of power output ends are arranged, walking cultivation power can be output through a secondary shaft, adaptive driving power can be provided through a second main shaft or additional machines with different secondary shafts, various speed changes can be realized, the problem that one mini-tiller serves as a power source, and the additional machines such as a water pump, a lawnmower, a grass cutter, a furrow opener and a spraying device which are driven by different rotation speeds can be driven to work normally by changing rotation speeds according to requirements is solved, and the requirements of users are met.
The invention is further described below with reference to the drawings and examples.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a block diagram of a sun gear;
FIG. 3 is an isometric view of a sun gear;
FIG. 4 is a block diagram of a planet carrier;
fig. 5 is a cross-sectional view taken along A-A of fig. 4.
Detailed Description
Referring to fig. 1 to 5, an embodiment of a power transmission mechanism of a mini-tiller gearbox comprises a main shaft and a secondary shaft. The main shaft comprises a first main shaft 3 and a second main shaft 15 which are positioned on the same axis, the first main shaft 3 is supported on the box body through a bearing, one end of the first main shaft 3 is fixedly connected with a sun gear 6 in the circumferential direction, the sun gear 6 is provided with an axially extending hollow shaft 6-3, and the hollow shaft 6-3 and the sun gear 6 are integrally processed and formed and can be fixedly connected with the sun gear 6 in the circumferential direction. One section of the shaft hole 6-4 of the hollow shaft is circumferentially fixed with the first main shaft 3, and the other section of the shaft hole is matched with the second main shaft 15 through a bearing. The sun gear 6 and the first main shaft 3 can be fixedly connected in the circumferential direction through a spline or in the circumferential direction through a key, and can also be connected in an interference fit manner; the other end of the first main shaft 3 is connected with an output shaft 1 of a mini-tiller power source through a clutch 2. The sun gear 6 is provided with external teeth 6-1 and joint internal teeth 6-2, the external teeth of the sun gear 6 are normally meshed with the planetary gears 4 supported on a planet carrier 7, and the planetary gears 4 are normally meshed with the inner gear ring 5 fixed on the box body to form a rotary planet carrier. The planet carrier 7 is provided with a plurality of planet gear supporting shafts 7-3 extending in the same direction, in this embodiment, three planet gear supporting shafts 7-3 are uniformly distributed on the planet carrier 7, more planet gear supporting shafts 7-3 can be arranged, each planet gear supporting shaft 7-3 is respectively and slidably matched with a planet gear 4, the planet gears 4 can be sleeved on the planet gear supporting shafts 7-3 in an empty mode, and can also be matched with the planet gear supporting shafts 7-3 through bearings. One end of the second main shaft 15 passes through a central hole 7-1 arranged on the planet carrier 7 and is supported in a shaft hole of the sun gear 6 through a bearing, the other end of the second main shaft 15 is supported in the box body through a bearing and is provided with an external additional tool, and in the embodiment, one end of the second main shaft 15, which is externally connected with the additional tool, is provided with a spline or a connecting flange, so that the connection with the additional tool is facilitated. The center hole 7-1 of the planet carrier 7 is provided with engaging internal teeth 7-2, the second main shaft 15 is in spline fit with an engaging tooth sleeve 8 capable of axially moving, one end of the engaging tooth sleeve 8 is provided with a first shifting fork clamping groove 8-1, the other end of the engaging tooth sleeve 8 is provided with engaging external teeth 8-2, the first shifting fork clamping groove 8-1 of the engaging tooth sleeve 8 is matched with a first shifting fork 9, the engaging external teeth 8-2 of the engaging tooth sleeve 8 can be meshed with the engaging internal teeth 7-2 of the planet carrier 7 through the shifting fork 9, or can be meshed with the engaging internal teeth of the sun gear 6, and the first main shaft 3 can transmit different torques to the second main shaft 15 through shifting. Alternatively, the engaging internal teeth 7-2 of the carrier 7 and the engaging internal teeth 6-2 of the sun gear 6 have a neutral space therebetween, and the engaging external teeth 8-2 of the engaging sleeve 8 are in the neutral position when the engaging external teeth 8-2 correspond to the neutral space therebetween of the carrier 7 and the engaging internal teeth of the sun gear 6. For this purpose, the central bore 7-1 of the planet carrier 7 can be divided into a bore section of the coupling internal tooth 7-2 and a relief bore section 7-4, the relief bore section 7-4 being located at one end of the planet carrier shaft 7-3 for relief of the coupling external tooth 8-2 of the coupling sleeve 8. When the first fork 9 pulls the engaging tooth sleeve 8 to enable the engaging external teeth 8-2 of the engaging tooth sleeve 8 to be located in the yielding hole section 7-4 provided in the central hole 7-1 of the planet carrier 7, that is, a neutral gear spacing is left between the engaging internal teeth of the planet carrier 7 and the sun gear 6, the engaging external teeth 8-2 of the engaging tooth sleeve 8 are in a neutral gear position, so that the power transmission from the first main shaft 3 to the second main shaft 15 can be interrupted. The second main shaft 15 is also in spline fit with a duplex driving gear 10 capable of axially moving, a second shifting fork clamping groove 10-3 is arranged between a first driving tooth 10-1 and a second driving tooth 10-2 of the duplex driving gear 10, the second shifting fork clamping groove 10-3 is matched with a second shifting fork 11, and the diameters of the first driving tooth 10-1 and the second driving tooth 10-2 are different. The auxiliary shaft 16 is supported on the box body in parallel with the second main shaft 15 through a bearing, one end of the auxiliary shaft 16 is provided with an output bevel gear 18, the bevel gear 18 is used for meshing with a transmission shaft of a mini-tiller walking system to transmit walking or tillage power of the tiller, the other end of the auxiliary shaft 16 is provided with an external additional machine, and in the embodiment, one end of the auxiliary shaft 16, which is externally connected with the additional machine, is provided with a spline or a connecting flange, so that the auxiliary shaft is convenient to connect with the additional machine. The auxiliary shaft 16 is fixedly connected with a duplex driven gear 17, and the diameters of the first driven tooth 17-1 and the second driven tooth 17-2 of the duplex driven gear 17 are different. The double driving gear 10 is shifted by the second shifting fork 11, so that the first driving gear 10-1 of the double driving gear 10 is meshed with the first driven gear 17-1 of the double driven gear 17, or the second driving gear 10-2 of the double driving gear 10 is meshed with the second driven gear 17-2 of the double driven gear 17, different torques are transmitted, or the double driving gear 10 is disengaged from the double driven gear 17, the first driving gear 10-1 of the double driving gear 10 and the first driven gear 17-1 of the double driven gear 17 are in a speed reduction transmission ratio, and the second driving gear 10-2 of the double driving gear 10 and the second driven gear 17-2 of the double driven gear 17 are in another speed reduction transmission ratio. And a neutral gear distance larger than the axial length of the duplex driving gear 10 is reserved between the first driven tooth 17-1 and the second driven tooth 17-2 of the duplex driven gear 17, and when the duplex driving gear 10 corresponds to the neutral gear distance, the duplex driving gear 10 does not transmit torque to the duplex driven gear 17. A reverse gear shaft 14 is supported on the box body and is parallel to the second main shaft 15, and a duplex reverse gear 12 is sleeved on the reverse gear shaft 14. One end of the duplex reverse gear 12 is provided with a third shifting fork clamping groove 12-3, the third shifting fork clamping groove 12-3 is matched with the third shifting fork 13, the other end of the third shifting fork clamping groove is provided with a first gear 12-1 and a second gear 12-2, the first gear 12-1 is used for being meshed with the second driving tooth 10-2 of the duplex driving gear 10, and the second gear 12-2 is used for being meshed with the second driven tooth 17-2 of the duplex driven gear 17. The duplex reverse gear 12 is shifted by the third shifting fork 13, so that the first gear 12-1 of the duplex reverse gear 12 is meshed with the second driving gear 10-2 of the duplex driving gear 10, the second gear 12-2 of the duplex reverse gear 12 is meshed with the second driven gear 17-2 of the duplex driven gear 17, and reverse gear torque is transmitted.
The box body of the power transmission mechanism can be designed into two parts, is very convenient to install and disassemble and repair the components in the box body, and can greatly reduce the workload.
The working condition of the power transmission mechanism of the gearbox of the mini-tiller is as follows: the clutch 2 transmits the power of the engine to the first main shaft 3, the first main shaft 3 drives the sun gear 6 to rotate, the sun gear 6 drives the planet gears 4 to rotate, and the planet gears 4 drive the planet carrier 7 to rotate.
The first shifting fork 9 is shifted to drive the engaging gear sleeve 8 to slide leftwards on the second main shaft 15, the engaging external teeth 8-2 of the engaging gear sleeve 8 are meshed with the engaging internal teeth 6-2 on the sun gear 6, the second main shaft 15 synchronously rotates along with the sun gear 6, the second main shaft 15 outputs a first rotating speed ZR1, and the rotating speed can meet the requirement of a first additional machine tool for directly taking force from the second main shaft 15.
The first shifting fork 9 is shifted to drive the engaging gear sleeve 8 to slide rightwards on the second main shaft 15, the engaging external teeth 8-2 of the engaging gear sleeve 8 and the engaging internal teeth 7-2 of the planet carrier 7 are synchronously rotated along with the planet carrier 7, so that the second main shaft 15 outputs a second rotating speed ZR2, and the rotating speed can meet the requirement of a second additional machine tool for directly taking force from the second main shaft 15.
Under the working condition of the first rotating speed ZR1 output by the second main shaft 15, the second shifting fork 11 is shifted to drive the duplex driving gear 10 to slide leftwards, the first driving gear 10-1 on the duplex driving gear 10 is meshed with the first driven gear 17-1 of the duplex driven gear 17, and the duplex driven gear 17 drives the auxiliary shaft 16 to rotate, so that the auxiliary shaft 16 outputs the first rotating speed FR1, and the rotating speed can be suitable for the requirement of a third additional machine tool for taking force from the auxiliary shaft 16.
Under the working condition that the second main shaft 15 outputs the first rotating speed ZR1, the second shifting fork 11 is shifted to drive the duplex driving gear 10 to slide rightwards, the second driving gear 10-2 on the duplex driving gear 10 is meshed with the second driven gear 17-2 of the duplex driven gear 17, the duplex driven gear 17 drives the auxiliary shaft 16 to rotate, so that the second rotating speed FR2 output by the shaft 16 can be adapted to the requirement of a fourth additional machine tool for taking force from the auxiliary shaft 16.
Under the working condition that the second main shaft 15 outputs the second rotating speed ZR2, the second shifting fork 11 is shifted to drive the duplex driving gear 10 to slide leftwards, the first driving gear 10-1 on the duplex driving gear 10 is meshed with the first driven gear 17-1 of the duplex driven gear 17, and the first driven gear 17-1 of the duplex driven gear 17 drives the auxiliary shaft 16 to rotate, so that the auxiliary shaft 16 outputs the third rotating speed FR3, and the rotating speed can meet the requirement of a fifth additional machine tool for taking force from the auxiliary shaft 16.
Under the working condition that the second main shaft 15 outputs the second rotating speed ZR2, the second shifting fork 11 is shifted to drive the duplex driving gear 10 to slide rightwards, the second driving gear 10-2 on the duplex driving gear 10 is meshed with the second driven gear 17-2 of the duplex driven gear 17, and the duplex driven gear 17 drives the auxiliary shaft 16 to rotate, so that the auxiliary shaft 16 outputs the fourth rotating speed FR4 which can be suitable for the requirement of a sixth additional tool for taking force from the auxiliary shaft 16.
Under the working condition that the second main shaft 15 outputs the first rotating speed ZR1, the second shifting fork 11 is shifted to enable the duplex driving gear 10 to be positioned at the neutral gear interval vacancy of the duplex driven gear 17; the third shifting fork 13 is shifted to drive the duplex reverse gear 12 to slide leftwards, so that the first gear 12-1 of the duplex reverse gear 12 is meshed with the second driving gear 10-2 of the duplex driving gear 10, the second gear 12-2 of the duplex reverse gear 12 is meshed with the second driven gear 17-2 of the duplex driven gear 17, the duplex driving gear 10 drives the duplex driven gear 17 to rotate through the duplex reverse gear 12, and the duplex driven gear 17 drives the auxiliary shaft 16 to reversely rotate, so that the auxiliary shaft 16 outputs a fifth rotating speed FR5, namely a reverse gear rotating speed.
Under the working condition that the second main shaft 15 outputs the second rotating speed ZR2, the second shifting fork 11 is shifted to enable the duplex driving gear 10 to be positioned at the neutral gear interval vacancy of the duplex driven gear 17; the third shifting fork 13 is shifted to drive the duplex reverse gear 12 to slide leftwards, so that the first gear 12-1 of the duplex reverse gear 12 is meshed with the second driving gear 10-2 of the duplex driving gear 10, the second gear 12-2 of the duplex reverse gear 12 is meshed with the second driven gear 17-2 of the duplex driven gear 17, the duplex driving gear 10 drives the duplex driven gear 17 to rotate through the duplex reverse gear 12, and the duplex driven gear 17 drives the auxiliary shaft 16 to reversely rotate, so that the auxiliary shaft 16 outputs a sixth rotating speed FR6, namely another reverse rotating speed.
Under the working condition that the second main shaft 15 outputs the first rotating speed ZR1 or the second rotating speed ZR2, the second shifting fork 11 is shifted to enable the duplex driving gear 10 to be positioned at a neutral gear interval vacancy of the duplex driven gear 17; the third shifting fork 13 is shifted to enable the duplex reverse gear 12, the duplex driving gear 10 and the duplex driven gear 17 to be disengaged, the auxiliary shaft 16 is not powered, and the auxiliary shaft 16 forms a neutral gear; or, the first shifting fork 9 is shifted to enable the external joint teeth 8-2 of the joint gear sleeve 8 to be positioned in the yielding hole section 7-4 of the central hole 7-1 of the planet carrier 7, the external joint teeth 8-2 of the joint gear sleeve 8 are disengaged from the internal joint teeth 6-2 of the sun gear 6 and the internal joint teeth 7-2 of the planet carrier 7, the second main shaft 15 has no power input, and the second main shaft 15 forms a neutral gear.
When an operator operates the device and uses the second main shaft 15 as power to directly output, two gear rotating speeds ZR1 and ZR2 are correspondingly provided; when the auxiliary shaft 16 rotates forward to output power, four gear speeds FR1, FR2, FR3 and FR4 are correspondingly provided; when the counter shaft 16 is rotated reversely as power output, there are two reverse gear rotational speeds FR5 and FR6, respectively. After being connected with the walking driving operation part through the bevel gear 18 on the auxiliary shaft 16, the mini-tiller can form four forward gears with different speeds and two backward gears with different speeds. The power transmission mechanism of the mini-tiller gearbox can be widely suitable for the working requirements of external additional machines, provides a wider application range for users, provides more selection gears for the users, and is convenient for operators to use.
The present invention is not limited to the specific description of the embodiments described above, but rather, modifications, additions or substitutions are possible, without departing from the scope and spirit of the invention as disclosed in the accompanying claims.
Claims (10)
1. The utility model provides a little cultivator gearbox power transmission mechanism, includes main shaft, countershaft, its characterized in that: the main shaft comprises a first main shaft (3) and a second main shaft (15) which are positioned on the same axis, the first main shaft (3) is supported in a box body through a bearing, one end of the first main shaft (3) is fixedly connected with a sun gear (6) in the circumferential direction, the sun gear (6) is provided with external teeth (6-1) and engaging internal teeth (6-2), the external teeth of the sun gear (6) are meshed with a planetary gear (4) supported on a planet carrier (7), the planetary gear (4) is meshed with an inner gear ring (5) fixed in the box body, one end of the second main shaft (15) penetrates through a central hole (7-1) formed in the planet carrier (7) and is supported in the shaft hole of the sun gear (6) through a bearing, the other end of the second main shaft is supported in the box body through the bearing and is provided with an external additional machine tool, the engaging gear sleeve (8) and the duplex driving gear (10) are matched with a spline on the second main shaft (15), and the engaging gear sleeve (8) is meshed with the first shifting fork (9) through the first shifting fork, and can be meshed with the engaging internal teeth (6-2) of the sun gear (6) or the planet carrier (7-2) in different torque transmission modes; the auxiliary shaft (16) is supported on the box body in parallel with the second main shaft (15) through a bearing, a bevel gear (18) is arranged at one end of the auxiliary shaft (16), an external additional machine tool is arranged at the other end of the auxiliary shaft, a duplex driven gear (17) is fixedly connected to the auxiliary shaft (16), the duplex driving gear (10) is shifted by the second shifting fork (11), so that a first driving tooth (10-1) of the duplex driving gear (10) is meshed with the first driven tooth (17-1) of the duplex driven gear (17), or a second driving tooth (10-2) of the duplex driving gear (10) is meshed with the second driven tooth (17-2) of the duplex driven gear (17), different torques are transmitted, or the duplex driving gear (10) is disengaged from the duplex driven gear (17); a reverse gear shaft (14) is supported on the box body and is parallel to the second main shaft (15), a duplex reverse gear (12) is sleeved on the reverse gear shaft (14), the duplex reverse gear (12) is shifted by a third shifting fork (13), one gear of the duplex reverse gear (12) can be meshed with a second driving tooth (10-2) of the duplex driving gear (10), and the other gear is meshed with a second driven tooth (17-2) of the duplex driven gear (17) to transmit reverse gear torque.
2. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: the sun gear (6) is provided with an axially extending hollow shaft (6-3), one section of the shaft hole (6-4) of the hollow shaft is circumferentially fixed with the first main shaft (3), and the other section of the shaft hole is matched with the second main shaft (15) through a bearing.
3. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: the first driving tooth (10-1) of the duplex driving gear (10) and the first driven tooth (17-1) of the duplex driven gear (17) are in a speed reduction transmission ratio, and the second driving tooth (10-2) of the duplex driving gear (10) and the second driven tooth (17-2) of the duplex driven gear (17) are in another speed reduction transmission ratio.
4. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: a second shifting fork clamping groove (10-3) is formed between the first driving tooth (10-1) and the second driving tooth (10-2) of the duplex driving gear (10).
5. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: a neutral gear distance which is larger than the axial length of the duplex driving gear (10) is reserved between a first driven tooth (17-1) and a second driven tooth (17-2) of the duplex driven gear (17), and when the duplex driving gear (10) corresponds to the neutral gear distance, the duplex driving gear (10) does not transmit torque to the duplex driven gear (17).
6. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: one end of the duplex reverse gear (12) is provided with a third shifting fork clamping groove (12-3), the other end of the duplex reverse gear is provided with a first gear (12-1) and a second gear (12-2), the first gear (12-1) is used for being meshed with a second driving tooth (10-2) of the duplex driving gear (10), and the second gear (12-2) is used for being meshed with a second driven tooth (17-2) of the duplex driven gear (17).
7. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: one end of the engaging tooth sleeve (8) is provided with a first shifting fork clamping groove (8-1), the other end is provided with engaging external teeth (8-2), and the engaging external teeth (8-2) can be meshed with engaging internal teeth of the planet carrier (7) or the sun gear (6).
8. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: and a neutral gear spacing is reserved between the joint inner teeth (7-2) of the planet carrier (7) and the joint inner teeth (6-2) of the sun gear (6), and when the joint outer teeth (8-2) of the joint gear sleeve (8) correspond to the neutral gear spacing reserved between the joint inner teeth of the planet carrier (7) and the joint inner teeth of the sun gear (6), the joint gear sleeve (8) is in the neutral gear.
9. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: the planet carrier (7) is provided with a plurality of planet gear supporting shafts (7-3) extending in the same direction, a central hole (7-1) of the planet carrier (7) is divided into a hole section for connecting the inner teeth (7-2) and a yielding hole section (7-4), and the yielding hole section (7-4) is close to one end of the planet gear supporting shaft (7-3).
10. The mini-tiller gearbox power transmission mechanism of claim 1, characterized by: the first main shaft (3) is connected with an output shaft (1) of a mini-tiller power source through a clutch (2), and one end of the second main shaft (15) and one end of the auxiliary shaft (16) externally connected with an additional machine tool are provided with a spline or a connecting flange.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711217319.XA CN107781364B (en) | 2017-11-28 | 2017-11-28 | Power transmission mechanism of gearbox of mini-tiller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711217319.XA CN107781364B (en) | 2017-11-28 | 2017-11-28 | Power transmission mechanism of gearbox of mini-tiller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107781364A CN107781364A (en) | 2018-03-09 |
| CN107781364B true CN107781364B (en) | 2024-03-01 |
Family
ID=61429788
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711217319.XA Active CN107781364B (en) | 2017-11-28 | 2017-11-28 | Power transmission mechanism of gearbox of mini-tiller |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107781364B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108909426B (en) * | 2018-08-27 | 2024-03-01 | 吉林大学 | Double-motor coupling planetary gear type two-gear variable speed drive axle |
| CN109488732A (en) * | 2018-12-28 | 2019-03-19 | 重庆鑫源农机股份有限公司 | Transmission device, method of power transmission and the mini-tiller of dual rotary direction gearbox |
| CN113586676A (en) * | 2021-07-30 | 2021-11-02 | 东阳市联宜机电有限公司 | Double-clutch reduction gearbox |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6258002B1 (en) * | 1997-07-01 | 2001-07-10 | Steyr-Daimler-Puch Fahrzeugtechnik Ag & Co Kg | Two-stage transfer gear-box |
| CN101280826A (en) * | 2008-05-13 | 2008-10-08 | 华南理工大学 | Power shift type automatic transmission system |
| WO2013159720A1 (en) * | 2012-04-26 | 2013-10-31 | Xiang Yongchuan | Automatic transmission |
| JP2014238136A (en) * | 2013-06-07 | 2014-12-18 | 本田技研工業株式会社 | Power transmission |
| CN205089947U (en) * | 2015-10-23 | 2016-03-16 | 张书雷 | Plough owner's machine gearbox a little |
| CN107269782A (en) * | 2017-08-08 | 2017-10-20 | 邓进桃 | Mechanical gear formula ST |
| CN207261587U (en) * | 2017-11-28 | 2018-04-20 | 重庆帝勒金驰通用机械股份有限公司 | Gear box of micro-cultivator actuating unit |
-
2017
- 2017-11-28 CN CN201711217319.XA patent/CN107781364B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6258002B1 (en) * | 1997-07-01 | 2001-07-10 | Steyr-Daimler-Puch Fahrzeugtechnik Ag & Co Kg | Two-stage transfer gear-box |
| CN101280826A (en) * | 2008-05-13 | 2008-10-08 | 华南理工大学 | Power shift type automatic transmission system |
| WO2013159720A1 (en) * | 2012-04-26 | 2013-10-31 | Xiang Yongchuan | Automatic transmission |
| JP2014238136A (en) * | 2013-06-07 | 2014-12-18 | 本田技研工業株式会社 | Power transmission |
| CN205089947U (en) * | 2015-10-23 | 2016-03-16 | 张书雷 | Plough owner's machine gearbox a little |
| CN107269782A (en) * | 2017-08-08 | 2017-10-20 | 邓进桃 | Mechanical gear formula ST |
| CN207261587U (en) * | 2017-11-28 | 2018-04-20 | 重庆帝勒金驰通用机械股份有限公司 | Gear box of micro-cultivator actuating unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107781364A (en) | 2018-03-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107781364B (en) | Power transmission mechanism of gearbox of mini-tiller | |
| CN103291853B (en) | Power structure of engine gearbox body | |
| CN207261587U (en) | Gear box of micro-cultivator actuating unit | |
| CN211693393U (en) | Main and auxiliary gear box assembly of mini-tiller | |
| CN108293327B (en) | Boat tractor transmission system and control method | |
| CN2278332Y (en) | Forward and reverse rotating device for rotavator | |
| CN202360701U (en) | Speed change transmission route for walking and rice transplanting of high-speed rice transplanting machine | |
| CN203934288U (en) | A kind of transmission box for tiller assembly | |
| CN106576448B (en) | Multifunctional mini-tiller transmission mechanism | |
| CN115848129A (en) | Transmission system and electric tractor | |
| US4233857A (en) | Multiple speed transmission with auxiliary transfer drive | |
| CN211574195U (en) | Transmission mechanism of field management machine | |
| CN213776237U (en) | Variable speed transmission system of field management machine | |
| CN108547945A (en) | A kind of double dynamical controllable multidirectional power output device of input realization of tractor | |
| CN112449768A (en) | Rotary cultivator matched with walking tractor | |
| KR20170114484A (en) | Transmission of Agricultural Vehicle | |
| CN207437739U (en) | A kind of gearbox designs | |
| CN216867430U (en) | Four-wheel drive mini-tiller belt transmission case | |
| CN215214591U (en) | Six-shaft multifunctional steering wheel type tractor gearbox | |
| CN204095512U (en) | A kind of front driving mechanism of three-wheel plant protection car | |
| CN201362174Y (en) | Transmission device with shuttle-type gear for small and medium series wheeled tractor | |
| CN215648097U (en) | Transmission assembly for rotary cultivator | |
| CN217241280U (en) | Rotary tillage transmission system of electric mini-tiller | |
| CN216555175U (en) | Two kinds of input drive's quick-witted gearbox assembly of ploughing a little | |
| CN213907351U (en) | Rotary cultivator matched with walking tractor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |