CN112096806A

CN112096806A - Combined gearbox

Info

Publication number: CN112096806A
Application number: CN202011040432.7A
Authority: CN
Inventors: 熊宏佳; 熊俞智
Original assignee: Foshan V Plus Machinery Co ltd
Current assignee: Foshan V Plus Machinery Co ltd
Priority date: 2020-09-28
Filing date: 2020-09-28
Publication date: 2020-12-18

Abstract

The invention discloses a combined gearbox, which comprises an input module, a speed change module, an output module and a box body, wherein the speed change module comprises a driving shaft, a driven shaft and a gear shift mechanism, the driving shaft is sequentially sleeved with a first gear, a second gear, a third gear and a fourth gear along the axial direction, and the driven shaft is sequentially sleeved with a fifth gear, a sixth gear, a seventh gear and an eighth gear which are meshed with corresponding gears on the driving shaft along the axial direction; the gear shifting mechanism is clamped to a first annular groove on the third gear and a second annular groove on the sixth gear; a first transmission piece, a second transmission piece, a third transmission piece and a fourth transmission piece are respectively arranged between the third gear and the second gear as well as between the third gear and the fourth gear, and a sixth transmission piece, a fifth transmission piece, an eighth transmission piece and a seventh transmission piece are respectively arranged between the sixth gear and the fifth gear as well as between the sixth gear and the seventh gear. The combined gearbox of the invention provides more speed selections, has compact and simple structure, can shift gears according to requirements without disassembly and assembly, and has convenient and reliable speed change.

Description

Combined gearbox

Technical Field

The invention relates to the technical field of transmission, in particular to a combined gearbox.

Background

In daily production work, due to the influence of various factors such as wood material, thickness, required machining shape, cutting depth of a cutter and the like, in order to obtain a required speed section and meet the requirement of finer speed required by machining, a feeder generally needs at least 8 gears. The common feeder can only directly adjust the gear (fast and slow two gears) of the motor under the condition of the gear ratio set by a factory. When the speed beyond the factory set gear ratio is required to be obtained, the protective rear cover of the feeder needs to be disassembled, the transmission component needs to be disassembled, all components are installed again after the gear with the new gear ratio is replaced, and the new speed can be obtained. If the speed obtained by the replaced new gear ratio does not meet the actual use requirement of production, the disassembly and assembly steps need to be repeated, and the process is time-consuming and labor-consuming. Frequent disassembly increases maintenance costs and greatly affects feeder part life. There is a large amount of lubricating grease in the gear engagement position, dismantles the gear shift in-process grease and very easily reveals the pollution that causes operational environment, is mostly the timber finish machining place because of feeder place processing production environment, if timber is stained by the grease then can't normally get into next process. In addition, if the cleaned old grease is not properly treated, the environment is greatly polluted, and extra cost is also generated by refilling the grease after the grease is disassembled. The disassembly and assembly process also needs certain technical requirements in the professional field, and potential safety hazards can be left if the operation is improper. Professional tools are needed for dismounting, dismounting parts are complex, and efficiency is extremely affected.

The needs that the dismouting can shift gears the variable speed should not, needs a gearbox collocation in order to reach this requirement on the feeder, appears collocating the gearbox that uses on the feeder in the market, is the variable speed mode that the meshing is deviate from between the different grades of general adoption two-stage tower gear, and only two grades of variable speeds have satisfied the 8 fast demands of feeder, joins in marriage the fast shelves of motor and also can only reach four grades, and remaining gear still need dismantle the change gear and just can switch. And when the gear is shifted, the gear has the defects of gear beating, meshing failure, unsmooth shifting and the like. The four-gear combined gearbox for shifting gears and changing speed in the same mode is extremely complex, occupies large space, still has the defects of tooth hitting, meshing failure, unsmooth gear shifting and the like, and is not suitable for being matched with a feeder with small volume.

The combined gearbox in the prior art is a purely mechanical four-gear gearbox of an electric vehicle, as described in an invention patent CN104373532A published in 25.2.2005, and four selectable speed gears are provided by sleeving sliding sleeve teeth sliding on different shafts with different gears, so that the segmentation of the feeding speed can be further refined if the combined gearbox can be used on a feeder, the fine requirement of a user on the speed section of the feeder can be met, the gear can be shifted without being disassembled and assembled, the speed change is convenient and fast, and the speed change efficiency is further improved. However, such a variable ratio coaxial compound transmission has the disadvantage of being bulky and space consuming in overall construction, and one of the gears is free of ratio, engagement-free and unrestrained (i.e. neutral), and in fact only provides three different ratios (i.e. three actual gears). In addition, the four-gear gearbox can only shift in a sequential forward mode or a sequential backward mode, and the four-gear gearbox cannot be randomly combined for shifting. Therefore, the gear shifting mechanism cannot be applied to a feeder to meet the requirement of 4-gear speed shifting.

Disclosure of Invention

In order to solve the technical problems, the invention provides a combined gearbox which provides more speed stage selections, has a compact and simple structure, can shift gears according to requirements without disassembly and assembly, and is convenient and reliable in speed change.

The technical problem solved by the invention is realized by adopting the following technical scheme: a combined gearbox comprises an input module, a speed change module, an output module and a box body, wherein the speed change module is installed in the box body, the input module comprises an input worm and a worm wheel, the input worm is meshed with the worm wheel, the speed change module comprises a driving shaft, a driven shaft and a gear shifting mechanism, the output module is fixedly arranged on the driven shaft, the worm wheel is fixedly arranged on the driving shaft, and the driving shaft is parallel to the driven shaft; the driving shaft is sequentially sleeved with a first gear fixed relative to the driving shaft, a second gear only rotatable relative to the driving shaft, a third gear only axially slidable relative to the driving shaft and rotating along with the driving shaft and a fourth gear only rotatable relative to the driving shaft, and the driven shaft is sequentially sleeved with a fifth gear only rotatable relative to the driven shaft, a sixth gear only axially slidable relative to the driven shaft and rotating along with the driven shaft, a seventh gear only rotatable relative to the driven shaft and an eighth gear fixed relative to the driven shaft; the first gear and the fifth gear, the second gear and the sixth gear, the third gear and the seventh gear, and the fourth gear and the eighth gear are meshed with each other in two groups, and the gear ratios are unequal; a first annular groove is formed in the third gear, a second annular groove is formed in the sixth gear, and the gear shifting mechanism is clamped to the first annular groove and the second annular groove; the opposite end surfaces of the third gear and the second gear are respectively provided with a first transmission piece and a second transmission piece which can be mutually nested, the opposite end surfaces of the third gear and the fourth gear are respectively provided with a third transmission piece and a fourth transmission piece which can be mutually nested, the opposite end surfaces of the sixth gear and the fifth gear are respectively provided with a sixth transmission piece and a fifth transmission piece which can be mutually nested, and the opposite end surfaces of the sixth gear and the seventh gear are respectively provided with an eighth transmission piece and a seventh transmission piece which can be mutually nested.

In the combined gearbox, the first gear is fixedly connected with the driving shaft, and the fifth gear on the correspondingly meshed driven shaft can rotate relative to the driven shaft and is limited in sliding along the axial direction; the second gear on the driving shaft can rotate relative to the driving shaft and is limited in sliding along the axial direction, and the sixth gear on the correspondingly meshed driven shaft can only slide along the axial direction relative to the driven shaft and cannot rotate; the third gear on the driving shaft can only slide along the axial direction relative to the driving shaft and can not rotate, and the seventh gear on the correspondingly meshed driven shaft can rotate relative to the driven shaft and is limited in sliding along the axial direction; the fourth gear on the driving shaft can rotate relative to the driving shaft and is limited in axial sliding, and the eighth gear on the corresponding meshed driven shaft is fixedly connected with the driven shaft.

The gear shifting mechanism is clamped to the first annular groove of the third gear and the second annular groove of the sixth gear to drive the third gear and the sixth gear to slide along the axial direction. The opposite end surfaces of the third gear and the second gear are respectively provided with a first transmission piece and a second transmission piece which can be mutually nested, the opposite end surfaces of the third gear and the fourth gear are respectively provided with a third transmission piece and a fourth transmission piece which can be mutually nested, the opposite end surfaces of the sixth gear and the fifth gear are respectively provided with a sixth transmission piece and a fifth transmission piece which can be mutually nested, and the opposite end surfaces of the sixth gear and the seventh gear are respectively provided with an eighth transmission piece and a seventh transmission piece which can be mutually nested. The third gear is a first positive position when sliding to the nesting of the first transmission piece and the second transmission piece and the separation of the third transmission piece and the fourth transmission piece, a first zero position when sliding to the separation of the first transmission piece and the second transmission piece and the separation of the third transmission piece and the fourth transmission piece, and a first negative position when sliding to the nesting of the third transmission piece and the fourth transmission piece and the separation of the first transmission piece and the second transmission piece. The first positive position is when the sixth gear slides to the nesting of the sixth transmission piece and the fifth transmission piece and the eighth transmission piece is separated from the seventh transmission piece, the second zero position is when the sixth gear slides to the nesting of the sixth transmission piece and the fifth transmission piece and the eighth transmission piece is separated from the seventh transmission piece, and the second negative position is when the sixth gear slides to the nesting of the eighth transmission piece and the seventh transmission piece and the sixth transmission piece is separated from the fifth transmission piece.

Power is input from an input worm of the input module, a worm wheel is meshed and matched with the input worm, and the worm wheel and the driving shaft are integrally driven to rotate around the axis. The first gear rotates along with the driving shaft at the same speed, the first gear is meshed with the fifth gear, the first gear drives the fifth gear to rotate, the sixth gear is located at the second positive position, the third gear is located at the first zero position, a sixth transmission element on the sixth gear is nested with a fifth transmission element on the fifth gear, the fifth gear drives the sixth gear to rotate at the same speed, the sixth gear and the driven shaft rotate integrally at the same speed, and the output module on the driven shaft outputs the speed which is the first speed-changing output mode (the first gear). When the third gear is located at the first positive position, the sixth gear is located at the second zero position, the driving shaft drives the third gear to rotate, the first transmission piece on the third gear is nested with the second transmission piece on the second gear, so that the third gear drives the second gear to rotate at the same speed, the second gear is meshed with the sixth gear, the second gear drives the sixth gear to rotate, the sixth gear and the driven shaft rotate integrally at the same speed, the output module on the driven shaft outputs the rotating speed, and at the moment, a second variable speed output mode (second gear) is adopted. When the sixth gear is located at the second negative position, the third gear is located at the first zero position, the driving shaft drives the third gear to rotate, the third gear is meshed with the seventh gear, so that the third gear drives the seventh gear to rotate, an eighth transmission member on the sixth gear is nested with a seventh transmission member on the seventh gear, so that the seventh gear drives the sixth gear to rotate at the same speed, the sixth gear and the driven shaft rotate integrally at the same speed, and the output module on the driven shaft outputs the rotating speed, namely, a third variable speed output mode (third gear). When the third gear is located at the first negative position, the sixth gear is located at the second zero position, the driving shaft drives the third gear to rotate, a third transmission piece on the third gear and a fourth transmission piece on the fourth gear are nested, so that the third gear drives the fourth gear to rotate at the same speed, the fourth gear is meshed with the eighth gear, the fourth gear drives the eighth gear to rotate, the eighth gear and the driven shaft rotate at the same speed integrally, the output module on the driven shaft outputs the rotating speed, and at the moment, the fourth variable speed output mode (fourth gear) is adopted. The gear ratios of the four pairs of the first gear and the fifth gear, the second gear and the sixth gear, the third gear and the seventh gear, and the fourth gear and the eighth gear are not equal to each other. The combined gearbox provides a speed gear of four gears, and can meet the requirement of more accurate speed. Moreover, the gear shifting operation can be carried out without disassembling and assembling the box body, and the gear shifting is convenient and fast. This combined type gearbox has still adopted the transmission medium nested to break away from the combination selection drive formula variable speed simultaneously, the meshing of old tower gear train and the variable speed that deviates from generally occupy space very, simultaneously the problem of bumping the tooth and collapsing the tooth takes place easily before gear and gear engagement when the gear shift, lead to the work piece to damage and variable speed unsmooth, and this combined type gearbox has adopted the transmission medium nested or the combination that breaks away from to select drive formula variable speed to replace the meshing of old tower gear train and the variable speed mode that deviates from, need not deviate from through the gear and again mesh can carry out the gear shift variable speed, structurally saved the space, the structure is compacter and simpler, select to drive the drawback of effectively avoiding old variable speed mode through the combination of transmission medium simultaneously, the variable speed is more smooth, and more convenient and reliable.

Preferably, gearshift includes the shift shaft, first gear shift fork, second gear shift fork and follower, the shift shaft is parallel with the driven shaft, first gear shift fork and second gear shift fork cup joint to the shift shaft, first gear shift fork block is to first ring channel, second gear shift fork block is to the second ring channel, the shift shaft has set gradually first cylinder cam groove and second cylinder cam groove along the axial, driven hole has all been seted up on first gear shift fork and the radial surface of second gear shift fork, the follower passes respectively in first cylinder cam groove and the second cylinder cam groove of driven hole card income on first gear shift fork and the second gear shift fork.

After the shift shaft starts to rotate, the first shift fork and the second shift fork start to perform axial displacement along with the tracks of the first cylindrical cam groove and the second cylindrical cam groove on the shift shaft, and the first shift fork and the second shift fork are clamped to the first annular groove on the third gear and the second annular groove on the sixth gear, so that the third gear and the sixth gear are driven to axially displace, and the required shift action is completed. The shift shaft provides a lateral positioning function for the first and second shift forks, controlling the distances of the first and second shift forks to the driving and driven shafts. Simultaneously, support for the first gear shifting fork and the second gear shifting fork is provided, and the first gear shifting fork and the second gear shifting fork are better nested to the first annular groove and the second annular groove. Because need let third gear and sixth gear satisfy relative position relation each other when first gear shift fork and the gear shift of second gear shift fork, the orbit in first cylinder cam groove and second cylinder cam groove can let first gear shift fork and second gear shift fork satisfy the required position requirement of gear shift. The driven member allows the first and second shift forks to be displaced axially on the shift shaft and according to a desired trajectory.

Preferably, the gear shifting mechanism further comprises a clamping piece, the first gear shifting fork and the second gear shifting fork are respectively provided with a clamping groove at the axial position corresponding to the driven hole, and the clamping piece is clamped to the clamping grooves and covers the driven hole. The clamping piece can effectively prevent the driven piece from loosening, and the first gear shifting fork and the second gear shifting fork can be better arranged on the gear shifting shaft and can perform axial displacement according to a required track.

Still preferably, the first cylinder cam groove has a first positive, a first zero, and a first negative axial displacement position with respect to the shift shaft, the second cylinder cam groove has a second positive, a second zero, and a second negative axial displacement position with respect to the shift shaft, and the axial displacement positions of the first cylinder cam groove and the second cylinder cam groove are in a logically self-locking relationship with each other. The first cylinder cam groove and the second cylinder cam groove have axial displacement positions which are in a logic self-locking relation with each other, and the axial displacement positions of the first cylinder cam groove and the second cylinder cam groove enable the first gear shifting fork and the second gear shifting fork to meet the position requirement required by gear shifting.

Preferably, the first transmission member and the second transmission member, the third transmission member and the fourth transmission member, the sixth transmission member and the fifth transmission member, and the eighth transmission member and the seventh transmission member, which are capable of being nested with each other, are of a plurality of equally-divided concave-convex structures between end surfaces of each other, are nested with each other in a concave-convex manner and have a virtual space, and when nested with each other, can be restricted from rotating with each other. First driving medium and second driving medium, third driving medium and fourth, sixth driving medium and fifth driving medium, eighth driving medium and seventh driving medium are the concave-convex structure of a plurality of equallys between the terminal surface each other, and the concave-convex structure between the terminal surface each other is nested, and concave-convex structure has the virtual position interval to be convenient for concave-convex structure to realize nesting each other, when concave-convex structure nests each other, restricts their mutual rotation each other.

In one embodiment, a positioning disc and a shifting knob are sequentially and fixedly arranged at the end part of the shifting shaft along the axial direction, a supporting hole is formed in the end face of the box body, which is close to the end part of the shifting shaft, a spring plunger is arranged in the supporting hole, a positioning hole is formed in the end face of the positioning disc, which faces the box body, and the spring plunger can be clamped into the positioning hole. The spring plunger is fixedly installed in the supporting hole, the steel ball of the spring plunger abuts against a positioning hole formed in the positioning disc to position the rotating position of the gear shifting shaft, when the gear shifting shaft rotates, the steel ball is separated from the positioning hole and abuts against the end face of the positioning disc to continue to rotate the gear shifting shaft to the next variable speed output mode (namely the next gear), the positioning hole formed in the positioning disc continues to be aligned with the spring plunger, and the steel ball is clamped into the positioning hole again to be positioned, so that the required gear can be selected by random rotation. Therefore, the alignment of the rotation positions of the shift shaft after gear shifting can be ensured, and the accuracy of the transverse positions of the first gear shifting fork and the second gear shifting fork when the required gears are reached is ensured.

In one embodiment, the third gear is keyed to the drive shaft, the third gear is axially slidable relative to the drive shaft and rotationally fixed relative to the drive shaft, the sixth gear is keyed to the driven shaft, and the sixth gear is axially slidable relative to the driven shaft and rotationally fixed relative to the driven shaft. The third gear can realize with the driving shaft key-type connection that the third gear slides along the driving shaft axial to can transmit the rotational speed of driving shaft to the third gear through the key-type connection. The sixth gear is in key connection with the driven shaft, so that the sixth gear can slide along the axial direction of the driving shaft, and the rotating speed of the sixth gear can be transmitted to the driven shaft through the key connection.

In one embodiment, the output module includes an output member, the driven shaft protruding out of the cover toward an end of the cover, the output member being mounted on the end of the protruding cover. The rotating speed of the driven shaft after speed change is output through the output part, the output part is arranged at the end part protruding out of the box cover and is out of the box body, other transmission parts are conveniently matched and used on the output part, and the output part can be used as output power to drive other parts.

In one embodiment, the box body comprises a shell, a box cover and a positioning screw, wherein the shell and the box cover are provided with a positioning pin hole, and the positioning screw with a positioning pin rod penetrates through the positioning pin hole for positioning and fastening. The box body can be formed by combining the shell body and the box cover, the disassembly, the assembly and the maintenance are convenient, and the positioning screw with the positioning pin rod penetrates through the positioning pin hole to compress the shell body and the box body together and can accurately and transversely position the positions of the shell body and the box cover.

Compared with the prior art, the invention has the beneficial effects that: more speed section selections are provided, the structure is compact and simple, gear shifting can be carried out according to needs without dismounting, and the speed change is more convenient and reliable.

Drawings

FIG. 1 is a schematic view of a feeder with a combination gearbox;

FIG. 2 is a schematic illustration in partial cross-section of a compound transmission;

FIG. 3 is a schematic view of the internal construction of the combiner gearbox;

FIG. 4 is an exploded assembly schematic of the combiner gearbox;

FIG. 5 is a schematic illustration of gear selection for the combiner gearbox;

fig. 6 is a schematic diagram of a shift mechanism of the combiner gearbox.

The drawings are for illustration purposes only and are not to be construed as limiting the invention; for a better understanding of the embodiments, certain features of the drawings may be omitted, enlarged or reduced, and do not represent actual product dimensions; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.

Detailed Description

The present invention will be further described with reference to the following detailed description and the accompanying drawings, but the present invention is not limited to the specific examples.

As shown in fig. 1, 2, 3 and 4, the compound transmission 100 includes an input module 10 (a motor in the present embodiment), a transmission module 20, an output module 30 and a case 50. As shown in fig. 4, the case 50 is composed of a case 510 and a case cover 530, and a gasket 520 is disposed at a joint plane of the case 510 and the case cover 530. Positioning pin holes 532 are formed in the shell 510 and the box cover 530, fixing holes 533 are formed in the box cover 530, and threaded holes are formed in positions corresponding to the shell 510; a set screw (e.g., shoulder screw) 550 with a set pin shaft passes through the set pin hole 532 and a screw 540 passes through the fixing hole 533 to lock and press-fit and laterally position the housing 510 and the cover 530. The input worm 110 is disposed within the housing 510. Three driving shafts 210, driven shafts 310 and shift shafts 410 are provided in parallel in the housing 50. The first gear 230, the second gear 240, the third gear 250 and the fourth gear 260 are sequentially sleeved on the driving shaft 210 along the axial direction, and the fifth gear 330, the sixth gear 340, the seventh gear 350 and the eighth gear 360 are sequentially sleeved on the driven shaft 310 along the axial direction. The first gear 230 is engaged with the fifth gear 330, the second gear 240 is engaged with the sixth gear 340, the third gear 250 is engaged with the seventh gear 350, and the fourth gear 260 is engaged with the eighth gear 360.

As shown in fig. 4, starting in the axial direction, the first gear 230 on the driving shaft 210 and the driving shaft 210 are mounted at the first step 211 through a key fixed connection (in this embodiment, a key fixed connection), the fifth gear 330 on the correspondingly engaged driven shaft 310 is mounted at the sixth step 311 on the driven shaft 310, and the fifth gear 330 is rotatable relative to the driven shaft 310 and is limited in axial sliding; the second gear 240 on the driving shaft 210 is mounted at the third step 213, the second gear 240 is rotatable with respect to the driving shaft 210 while being restricted in axial sliding, and the sixth gear 340 on the driven shaft 310, which is correspondingly engaged, is mounted at the seventh step 312. In this embodiment, the seventh step 312 of the driven shaft 310 is a spline shaft, the inner hole of the sixth gear 340 is an inner spline hole, and the spline shaft and the inner spline hole are matched with each other to make the sixth gear 340 only axially slide but not rotate relative to the driven shaft 310; the third gear 250 on the driving shaft 210 is mounted at the fourth step 214, in this embodiment, the fourth step 214 is a spline shaft, an inner hole of the third gear 250 is an inner spline hole, the spline shaft and the inner spline hole are matched with each other, so that the third gear 250 can only axially slide and cannot rotate relative to the driving shaft 210, the seventh gear 350 on the driven shaft 310, which is correspondingly engaged, is mounted at the eighth step 313, and the seventh gear 350 can only rotate and is limited in axial sliding relative to the driven shaft 310; the fourth gear 260 on the driving shaft 210 is mounted at the fifth step 215, the fourth gear 260 is rotatable with respect to the driving shaft 210 while being restricted in axial sliding, and the eighth gear 360 on the driven shaft 310, which is correspondingly engaged, is mounted at the ninth step 314 by fixed connection (in the present embodiment, key fixed connection) with the driven shaft 310.

As shown in fig. 4 and 6, the transmission module 20 includes a shift mechanism 40, and the shift mechanism 40 includes a shift spindle 410, a first shift fork 460, a second shift fork 440, and a follower 450. The shift spindle 410 is provided with a first cylinder cam groove 411 and a second cylinder cam groove 412 at a pitch in the middle of the radial surface thereof which varies in axial regular displacement. One ends of the first and

second shift forks

460 and 440 are respectively a first sleeve 461 and a second sleeve 441, and the other ends of the first and

second shift forks

460 and 440 are respectively a first fork end 462 of a semicircular open fork shape and a second fork end 442 of a semicircular open fork shape. The first sleeve 461 of the first shift fork 460 and the second sleeve 441 of the second shift fork 440 are respectively sleeved on the first cylinder cam groove 411 and the second cylinder cam groove 412 of the shift spindle 410. The radial surfaces of the first sleeve 461 and the second sleeve 441 are correspondingly provided with driven

holes

464 and 444, the driven

holes

464 and 444 are penetrated from the outer wall to the inner wall of the first sleeve 461 and the second sleeve 441, the driven piece 450 is arranged in the driven

holes

464 and 444, the driven piece 450 corresponding to the first shift fork 460 and the second shift fork 440 is clamped into the corresponding first cylinder cam groove 411 and the second cylinder cam groove 412, and the first shift fork 460 and the second shift fork 440 are respectively changed along with the axial displacement of the first cylinder cam groove 411 and the second cylinder cam groove 412 so as to drive the third gear 250 and the sixth gear 340 to axially displace along with the axial displacement. The third gear 250 and the sixth gear 340 are correspondingly provided with a first annular groove 251 and a second annular groove 341, and a first fork end 462 of the first shift fork 460 is clamped in the first annular groove 251 of the third gear 250, so that the third gear 250 is pulled to axially slide but is not blocked from rotating. The second fork end 442 of the second shift fork 440 is engaged in the second annular groove 341 of the sixth gear 340 to pull the sixth gear 340 to slide axially without hindering its rotation. The first shift fork 460 is provided with a through hole 465 in the middle thereof so as not to interfere with the driven shaft 310 and the gears on the driven shaft 310. The diameter of the through hole 465 is larger than the addendum circle of the seventh gear 350. The first and

second sleeves

461 and 441 are provided with first and second catching

grooves

463 and 443, respectively, corresponding to the follower holes 464 and 444, and the gearshift mechanism 40 further includes a catching member 430, the catching member 430 catching on the first and second catching

grooves

463 and 443, and restricting the follower 450 from coming out.

As shown in fig. 4 and 5, four positioning holes 571 are uniformly distributed on the circumference of the end surface of the positioning plate 570 mounted on the shift spindle 410 facing the box cover 530, two support holes 531 are symmetrically arranged on the end surface of the box cover 530 at 180 degrees concentric with the shift spindle 410, two spring plungers 560 are mounted and fixed in the support holes 531, steel balls of the spring plungers 560 abut against the positioning holes 571 arranged on the positioning plate 570 to position the shift spindle 410, when the shift spindle 410 is rotated, the steel balls are disengaged from the positioning holes 571 and abut against the end surface of the positioning plate 570, the shift spindle 410 is continuously rotated to the next gear, the positioning holes 571 arranged on the positioning plate 570 are aligned with the spring plungers 560 again, and the steel balls are clamped into the positioning holes 571 again to position. The positioning plate 570 is fixedly coupled (in this embodiment, a key fixedly coupled) to the shift spindle 410, and the shift knob 580 is fixed to the shift spindle 410 by a screw spring washer 590.

As shown in fig. 4 and 6, a plurality of equally spaced first transmission members 252 and third transmission members 253 are provided on both end surfaces of the third gear 250 in the axial direction, and a plurality of equally spaced second transmission members 241 and a plurality of equally spaced fourth transmission members 261 are provided on end surfaces of the second gear 240 and the fourth gear 260 facing the third gear 250, respectively. Both end surfaces of sixth gear 340 in the axial direction are provided with a plurality of equally spaced sixth transmission members 342 and eighth transmission members 343, and end surfaces of fifth gear 330 and seventh gear 350 facing sixth gear 340 are provided with a plurality of equally spaced fifth transmission members 331 and a plurality of equally spaced seventh transmission members 351, respectively.

First and

second shift forks

460 and 440 are movable in response to axial displacement of first and second

cylinder cam slots

411 and 412 to drive third and

sixth gears

250 and 340 for corresponding axial displacement. The first positive position is when the third gear 250 slides until the first transmission member 252 is nested with the second transmission member 241 and the third transmission member 253 is disengaged from the fourth transmission member 261, the first zero position is when the third gear 250 slides until the first transmission member 252 is disengaged from the second transmission member 241 and the third transmission member 253 is disengaged from the fourth transmission member 261, and the first negative position is when the third gear 250 slides until the third transmission member 253 is nested with the fourth transmission member 261 and the first transmission member 252 is disengaged from the second transmission member 241. A second positive position when sixth gear 340 slides until sixth transmission member 342 is nested with fifth transmission member 331 and eighth transmission member 343 is disengaged from seventh transmission member 351, a second null position when sixth gear 340 slides until sixth transmission member 342 is disengaged from fifth transmission member 331 and eighth transmission member 343 is disengaged from seventh transmission member 351, and a second negative position when sixth gear 340 slides until eighth transmission member 343 is nested with seventh transmission member 351 and sixth transmission member 342 is disengaged from fifth transmission member 331.

As shown in fig. 3, 4 and 5, a worm wheel 120 is sleeved between the first gear 230 and the second gear 240 on the driving shaft 210, the worm wheel 120 is fixedly connected and installed at the second step 212, in this example, a clamp spring groove is provided between the worm wheel 120 and the second gear 240, a clamp spring 280 for a shaft is clamped in the clamp spring groove, and the clamp spring 280 for a shaft ensures that the worm wheel 120 does not contact or interfere with the second gear 240, thereby affecting the free rotation of the second gear relative to the driving shaft 210. The worm gear 120 is in meshing engagement with the input worm 110. The output member (in this embodiment, the output gear 610) is fixedly mounted on the driven shaft 310 by being keyed by a nut 620 and a flat washer 630, and the output gear 610 is disposed at the tenth step 315 of the driven shaft 310 toward and beyond the cover 530. When power is input from the input worm 110, the worm wheel 120 is integrally driven to rotate around the axis with the drive shaft 210.

When the shift knob 580 is rotated to the first gear position, the steel ball of the spring plunger 560 abuts against the positioning hole 571 disposed on the positioning plate 570 to position the shift spindle 410, the shift spindle 410 rotates to drive the first cylindrical cam groove 411 and the second cylindrical cam groove 412 on the shift spindle 410 to rotate synchronously, and the first shift fork 460 and the second shift fork 440 change along with the axial displacement of the first cylindrical cam groove 411 and the second cylindrical cam groove 412 to drive the third gear 250 and the sixth gear 340 to generate corresponding axial displacement, which is the first gear shift output mode at this time. In the first variable speed output mode, the first gear 230 rotates with the same rotation speed as the driving shaft 210, the first gear 230 drives the fifth gear 330 to rotate, at this time, the sixth gear 340 is located at the second positive position, the third gear 250 is located at the first zero position, the fifth gear 330 drives the sixth gear 340 to rotate at the same speed, the driven shaft 310 rotates integrally with the sixth gear 340 at the same speed through key connection, and the driven shaft 310 outputs power through the output gear 610 on the output end according to the changed rotation speed.

When the shift knob 580 is rotated to the second gear, the positioning hole 571 formed in the positioning plate 570 is disengaged from the spring plunger 560 and then realigned, the steel ball is locked into the next positioning hole 571 again for positioning, the shift spindle 410 rotates to drive the first cylindrical cam groove 411 and the second cylindrical cam groove 412 on the shift spindle 410 to rotate, the first shift fork 460 and the second shift fork 440 change along with the axial displacement of the first cylindrical cam groove 411 and the second cylindrical cam groove 412 to drive the third gear 250 and the sixth gear 340 to generate corresponding axial displacement, and at this time, the second gear shift output mode is adopted. In the second variable speed output mode, the third gear 250 is located at the first positive position, the sixth gear 340 is located at the second zero position, the driving shaft 210 drives the third gear 250 to rotate, the third gear 250 drives the second gear 240 to rotate at the same speed, the second gear 240 drives the sixth gear 340 to rotate, the driven shaft 310 is connected with the sixth gear 340 through a key to rotate at the same speed integrally, and the driven shaft 310 outputs power through the output gear 610 on the output end according to the variable speed.

When the shift knob 580 is rotated to the third gear, the positioning hole 571 formed in the positioning plate 570 is disengaged from the spring plunger 560 and then realigned, the steel ball is locked into the next positioning hole 571 again for positioning, the shift spindle 410 rotates to drive the first cylindrical cam groove 411 and the second cylindrical cam groove 412 on the shift spindle 410 to rotate, the first shift fork 460 and the second shift fork 440 change along with the axial displacement of the first cylindrical cam groove 411 and the second cylindrical cam groove 412 to drive the third gear 250 and the sixth gear 340 to generate corresponding axial displacement, and at this time, the third gear shift output mode is the third gear shift output mode. In the third variable speed output mode, the sixth gear 340 is located at the second negative position, the third gear 250 is located at the first zero position, the driving shaft 210 drives the third gear 250 to rotate, the third gear 250 drives the seventh gear 350 to rotate, the seventh gear 350 drives the sixth gear 340 to rotate at the same speed, the driven shaft 310 integrally rotates at the same speed with the sixth gear 340 through key connection, and the driven shaft 310 outputs power through the output gear 610 on the output end according to the variable speed.

When the shift knob 580 is rotated to the fourth gear, the positioning hole 571 formed in the positioning plate 570 is disengaged from the spring plunger 560 and then realigned, the steel ball is locked into the next positioning hole 571 again for positioning, the shift spindle 410 rotates to drive the first cylindrical cam groove 411 and the second cylindrical cam groove 412 on the shift spindle 410 to rotate, the first shift fork 460 and the second shift fork 440 change along with the axial displacement of the first cylindrical cam groove 411 and the second cylindrical cam groove 412 to drive the third gear 250 and the sixth gear 340 to generate corresponding axial displacement, and at this time, the fourth gear shift output mode is realized. In the fourth variable speed output mode, the third gear 250 is located at the first negative position, the sixth gear 340 is located at the second zero position, the driving shaft 210 drives the third gear 250 to rotate, the third gear 250 drives the fourth gear 260 to rotate at the same speed, the fourth gear 260 drives the eighth gear 360 to rotate, the eighth gear 360 is fixed on the driven shaft 310, so that the third gear 250 and the fourth gear 260 rotate at the same speed integrally and at the same speed, and the driven shaft 310 outputs power through the output gear 610 on the output end according to the variable speed.

As the rotation angle of the shift shaft 410 changes, the first shift fork 460 drives the third gear 250 to have three states, i.e., a first positive state, a first zero state, and a first negative state; the second shift fork 440 drives the sixth gear 340 to have three states, i.e., a second positive position, a second zero position, and a second negative position. First spur cam slot 411 and second spur cam slot 412 on shift shaft 410 are in a logical relationship in axial displacement change, and second shift fork 440 defines sixth gear 340 in a second zero position when first shift fork 460 drives third gear 250 to a first positive position or a first negative position; when second shift fork 440 drives sixth gear 340 to the second positive position or the second negative position, first shift fork 460 positions third gear 250 in the first zero position, such that first shift fork 460 and second shift fork 440 have an interlocking function. In this example, the gear combination sequence of the first gear, the second gear, the third gear and the fourth gear is the application of this embodiment, but the gear combination sequence of this application is not limited to the combination sequence of this embodiment, and it also belongs to this application scope to obtain a gear combination sequence different from this embodiment by adjusting the logical relationship between the first cylinder cam groove 411 and the second cylinder cam groove 412. The gear ratios of the four pairs of the first gear 230 and the fifth gear 330, the second gear 240 and the sixth gear 340, the third gear 250 and the seventh gear 350, and the fourth gear 260 and the eighth gear 360 are not equal to each other.

As shown in fig. 4, the first bearing 220 and the second bearing 270 are provided at both axial ends of the driving shaft 210, the third bearing 320 and the fourth bearing 370 are provided at both axial ends of the driven shaft 310, and the fifth bearing 420 and the sixth bearing 470 are provided at both axial ends of the shift shaft 410. The first bearing 220, the third bearing 320 and the fifth bearing 420 are fixed to the housing 510 at bearing

holes

513, 512, 511. The second bearing 270, the fourth bearing 370 and the sixth bearing 470 are fixed on the cover 530, and the driven shaft 310 and the shift shaft 410 have a shaft body at the end of the cover 530 beyond the bearing, and are respectively provided with a first sealing member 380 and a second sealing member 480, and the outer rings of the first sealing member 380 and the second sealing member 480 are matched with the cover 530 and the end surfaces are flush with the cover surface for sealing.

It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.

Claims

1. A combined gearbox comprises an input module, a speed change module, an output module and a box body, wherein the speed change module is arranged in the box body; the driving shaft is sequentially sleeved with a first gear fixed relative to the driving shaft, a second gear only rotatable relative to the driving shaft, a third gear only slidable in the axial direction relative to the driving shaft and a fourth gear only rotatable relative to the driving shaft, and the driven shaft is sequentially sleeved with a fifth gear only rotatable relative to the driven shaft, a sixth gear only slidable in the axial direction relative to the driven shaft, a seventh gear only rotatable relative to the driven shaft and an eighth gear fixed relative to the driven shaft; the first gear and the fifth gear, the second gear and the sixth gear, the third gear and the seventh gear, and the fourth gear and the eighth gear are meshed with each other in two groups, and the gear ratios are unequal; a first annular groove is formed in the third gear, a second annular groove is formed in the sixth gear, and the gear shifting mechanism is clamped to the first annular groove and the second annular groove; the opposite end surfaces of the third gear and the second gear are respectively provided with a first transmission piece and a second transmission piece which can be mutually nested, the opposite end surfaces of the third gear and the fourth gear are respectively provided with a third transmission piece and a fourth transmission piece which can be mutually nested, the opposite end surfaces of the sixth gear and the fifth gear are respectively provided with a sixth transmission piece and a fifth transmission piece which can be mutually nested, and the opposite end surfaces of the sixth gear and the seventh gear are respectively provided with an eighth transmission piece and a seventh transmission piece which can be mutually nested.

2. The combiner gearbox of claim 1, wherein the shift mechanism comprises a shift shaft, a first shift fork, a second shift fork and followers, the shift shaft is parallel to the driven shaft, the first shift fork and the second shift fork are sleeved on the shift shaft, the first shift fork is clamped to the first annular groove, the second shift fork is clamped to the second annular groove, the shift shaft is sequentially provided with a first cylindrical cam groove and a second cylindrical cam groove along the axial direction, driven holes are formed in radial surfaces of the first shift fork and the second shift fork, and the two followers respectively penetrate through the driven holes in the first shift fork and the second shift fork to be clamped into the first cylindrical cam groove and the second cylindrical cam groove.

3. The combiner gearbox of claim 2, wherein the shift mechanism further comprises a clamping member, the first shift fork and the second shift fork are respectively provided with a clamping groove at an axial position corresponding to the driven hole, and the clamping member is clamped to the clamping grooves and covers the driven hole.

4. The compound transmission of claim 2, wherein the first cylinder cam groove has a first positive, a first zero, and a first negative axial displacement position relative to the shift shaft, and the second cylinder cam groove has a second positive, a second zero, and a second negative axial displacement position relative to the shift shaft, the axial displacement positions of the first cylinder cam groove and the second cylinder cam groove being logically self-locking relative to each other.

5. A combiner gearbox according to claim 1 wherein the first and second, third and fourth, sixth and fifth, and eighth and seventh mutually nestable transmission members are of a plurality of equally concave and convex configurations between their end faces, each nested concave and convex with a virtual spacing therebetween, and when nested one within the other, restrict rotation relative to each other.

6. The compound transmission according to any one of claims 2 to 5, wherein a positioning plate and a shift knob are fixedly arranged on an end portion of the shift spindle in the axial direction in sequence, a support hole is formed in an end surface of the case body close to the end portion of the shift spindle, a spring plunger is arranged in the support hole, a positioning hole is formed in an end surface of the positioning plate facing the case body, and the spring plunger can be clamped in the positioning hole.

7. A combiner gearbox according to any one of claims 1 to 5 wherein the third gear is keyed to the drive shaft, the third gear is axially slidable relative to the drive shaft and non-rotatable relative to the drive shaft, the sixth gear is keyed to the driven shaft, the sixth gear is axially slidable relative to the driven shaft and non-rotatable relative to the driven shaft.

8. A combiner gearbox according to any of claims 1 to 5, characterised in that the output module comprises an output member, the driven shaft protruding out of the cover towards the end of the cover, the output member being mounted on the end of the protruding cover.

9. The combination gearbox according to any one of claims 1 to 5, wherein the casing comprises a casing, a cover and a set screw, the casing and the cover are provided with a set pin hole, and the set screw with a set pin rod is inserted into the set pin hole for positioning and fastening.