CN211398552U - Twelve-gear transmission with helical teeth and double intermediate shafts - Google Patents
Twelve-gear transmission with helical teeth and double intermediate shafts Download PDFInfo
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- CN211398552U CN211398552U CN201922441706.2U CN201922441706U CN211398552U CN 211398552 U CN211398552 U CN 211398552U CN 201922441706 U CN201922441706 U CN 201922441706U CN 211398552 U CN211398552 U CN 211398552U
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Abstract
The utility model relates to the field of transmissions, in particular to a twelve-gear transmission with helical teeth and double intermediate shafts.A main box comprises a first shaft, a second shaft, a main shifting fork shaft and a locking mechanism, wherein the second shaft is coaxial with the first shaft, two symmetrical intermediate shafts are arranged on two sides of the second shaft, and the main box is of a parallel shaft type transmission structure and comprises six forward gears and one reverse gear; the auxiliary box is internally provided with a planetary transmission structure which comprises a high gear and a low gear; the locking mechanism comprises a locking unit and an interlocking shaft, the interlocking shaft is perpendicular to the main shifting fork shaft, a limiting groove is formed in the circumferential surface of the main shifting fork shaft, a limiting block is arranged on the interlocking shaft, and the locking unit can clamp the limiting block into the limiting groove and pull out the limiting groove. When the technical scheme is adopted, the gears can be increased and the transmission stability can be improved.
Description
Technical Field
The utility model relates to a derailleur field, concretely relates to twelve grades of derailleurs of skewed tooth double countershaft.
Background
At present, the heavy truck type multi-gear automobile transmission with the auxiliary box and the multiple gears in China is mainly provided with 4-5 gears in the main box, the main box is mainly of a single-intermediate-shaft structure, and the transmission stability is relatively poor. Meanwhile, a driver can drive the main shifting fork shaft and the main shifting fork to move and drive the synchronizer to move to realize shifting of the main box by operating the shifting handle, the shifting condition of the main box is sensed when the shifting handle is operated, and shifting of the auxiliary box is realized by the air cylinder; if the auxiliary box can not be shifted, even if the driver shifts gears through the main box by the gear shifting handle, the gearbox can not transmit the rotating speed and the torque, and even the auxiliary box can be damaged.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a two jackshaft twelve-gear derailleur of skewed tooth that the conveying is stable can restrict the main tank gear shift during the auxiliary tank gear shift.
In order to achieve the above object, the technical solution of the present invention is to provide a dual-countershaft twelve-speed transmission with helical teeth, wherein a main box comprises a first shaft, a second shaft, a main shift fork shaft and a locking mechanism, the second shaft is coaxial with the first shaft, two symmetrical countershafts are arranged on two sides of the second shaft, and the main box is of a parallel shaft type transmission structure and comprises six forward gears and one reverse gear; the auxiliary box is internally provided with a planetary transmission structure which comprises a high gear and a low gear; the locking mechanism comprises a locking unit and an interlocking shaft, the interlocking shaft is perpendicular to the main shifting fork shaft, a limiting groove is formed in the circumferential surface of the main shifting fork shaft, a limiting block is arranged on the interlocking shaft, and the locking unit can clamp the limiting block into the limiting groove and pull out the limiting groove.
The technical effect of the scheme is as follows: the gear is more, the fuel economy is high, the transmission stability is high, and when the auxiliary box is in gear, the locking unit clamps the limiting block on the interlocking shaft into the limiting groove, and the limiting block can prevent the main shifting fork shaft from sliding along the axial direction of the main shifting fork shaft, so that the action of the main shifting fork shaft is avoided; when the auxiliary box is completely engaged, the limit blocks on the interlocking shafts slide out of the limit grooves under the action of the locking units, and the main shifting fork shaft can slide along the axial direction of the main shifting fork shaft, so that the main box does not perform gear shifting action when the auxiliary box is shifted, and the auxiliary box is prevented from being damaged.
Further, the main box also comprises an idle wheel, a first shaft constant mesh gear is fixedly arranged on the first shaft, and a middle shaft constant mesh gear, a middle shaft six-gear, a middle shaft four-gear, a middle shaft three-gear, a middle shaft two-gear and a middle shaft first-gear are fixedly arranged on the middle shaft in sequence; a second shaft six-gear, a second shaft four-gear, a second shaft three-gear, a second shaft two-gear, a second shaft first-gear and a second shaft reverse gear are fixedly arranged on the second shaft in sequence; the first shaft constant mesh gear is meshed with the intermediate shaft constant mesh gear, the intermediate shaft six-gear, the intermediate shaft four-gear, the intermediate shaft three-gear, the intermediate shaft second-gear and the intermediate shaft first-gear are correspondingly meshed with the second shaft six-gear, the second shaft four-gear, the second shaft third-gear, the second shaft second-gear and the second shaft first-gear, and the intermediate shaft first-gear can be meshed with the second shaft reverse gear through the idle gear; synchronizers are arranged between the first-gear of the second shaft and the second-gear of the second shaft, between the third-gear of the second shaft and the fourth-gear of the second shaft and on one side of the sixth-gear of the second shaft. The technical effect of the scheme is as follows: the main box has compact structure and large torque capacity, and can realize six forward gears and one reverse gear function through the synchronizer.
Furthermore, the auxiliary box comprises a planetary transmission mechanism, a pneumatic gear shifting mechanism, a power output shaft and a high-grade synchronous cone base, and the high-grade synchronous cone base is fixed on the power output shaft; the planetary transmission mechanism comprises a sun gear, a planet carrier, a planet gear and a gear ring, a support seat is sleeved on the power output shaft, and the support seat is connected with the gear ring into a whole through a spline; and a low-gear synchronous cone, a high-gear synchronous cone and a high-low gear synchronizer assembly controlled by the pneumatic gear shifting mechanism are arranged outside the supporting seat, and the high-low gear synchronizer assembly comprises a combination sleeve which can be meshed with the gear ring. The technical effect of the scheme is as follows: the auxiliary box has a high-low gear switching function, realizes multi-gear speed change under the linkage action of the main box and the auxiliary box, and has the characteristics of large bearing capacity, compact structure and large gear number.
Further, the synchronizer is a three-cone synchronizer. The technical effect of the scheme is as follows: the gear shifting force and the gear shifting time of the synchronizer are effectively reduced, the purpose of light gear shifting is achieved, meanwhile, due to the fact that the friction pairs are increased, the contact stress of the friction surface is greatly reduced, and the service life of the synchronizer is effectively prolonged.
Furthermore, the auxiliary box also comprises an auxiliary shifting fork shaft and an auxiliary shifting fork, wherein an ejector rod is fixed on the auxiliary shifting fork and is parallel to the main shifting fork shaft, and the ejector rod is driven by the auxiliary shifting fork shaft. The technical effect of the scheme is as follows: the ejector rod is directly fixed on the auxiliary shifting fork, so that the production is convenient.
Furthermore, the locking unit comprises a spring and a locking chute, the locking chute is arranged on the ejector rod, the spring is arranged at one end of the interlocking shaft, and the other end of the interlocking shaft can be in contact with the circumferential surface of the ejector rod or is positioned in the locking chute; the periphery of the main shifting fork shaft is provided with a limiting groove, the interlocking shaft is provided with a limiting block, and the limiting block and the limiting groove are close to one side of the spring. The technical effect of the scheme is as follows: when the auxiliary box is in gear, the ejector rod moves along the axial direction of the ejector rod, and under the action of the spring, the interlocking shaft slides into the locking chute from the contact with the circumferential surface of the ejector rod, so that the limiting block is clamped into the limiting groove, and the action of the main shifting fork shaft is avoided.
Furthermore, the locking unit comprises a first rack, a second rack and a gear column, the first rack is fixedly connected with the interlocking shaft, the second rack is fixedly connected with the ejector rod, and the first rack and the second rack are both meshed with the gear column; two opposite limiting grooves are arranged on the circumferential surface of the main shifting fork shaft, and two limiting blocks are arranged on the interlocking shaft. The technical effect of the scheme is as follows: when the auxiliary box is in gear shifting, the ejector rod moves along the axial direction of the auxiliary box, so that the gear column is driven to rotate through the second rack, the first rack and the interlocking shaft are driven to move, the limiting block is clamped into the limiting groove, and the action of the main shifting fork shaft is avoided; when the auxiliary shifting fork is in the middle position, the limiting blocks are separated from the limiting grooves, when the auxiliary shifting fork moves left and right under the action of the auxiliary shifting fork shaft, the two limiting blocks can intermittently lock the main shifting fork shaft, the problem of spring failure under the condition of using a spring does not exist, two opposite limiting grooves are arranged on the circumferential surface of the main shifting fork shaft, and compared with the situation that one limiting groove is arranged on the circumferential surface of the main shifting fork shaft, the weight distribution of the main shifting fork shaft is more uniform; because the main shifting fork shaft is provided with the limiting groove, the main shifting fork shaft can rotate around the circumferential direction of the main shifting fork shaft in the process of reciprocating sliding during gear shifting due to uneven gravity distribution, so that one side without the limiting groove rotates to the lower part; therefore, the main shifting fork shaft cannot rotate around the circumferential direction of the main shifting fork shaft, deviation of the main shifting fork cannot be caused, and smooth gear shifting is ensured.
Furthermore, an arc-shaped groove is formed in the circumferential surface of the interlocking shaft, and the main shifting fork shaft is located in the arc-shaped groove. The technical effect of the scheme is as follows: the space occupied by the main shifting fork shaft and the interlocking shaft in the longitudinal direction can be reduced.
Furthermore, the number of the locking chutes is two, and the distance between the locking chutes is smaller than the diameter of the interlocking shaft. The technical effect of the scheme is as follows: the instantaneity of the interlocking shaft inserted into the locking inclined groove during the gear shifting of the auxiliary box can be improved.
Furthermore, the friction surfaces of the low-grade synchronous cone and the high-grade synchronous cone are provided with carbon particle layers. The technical effect of the scheme is as follows: the friction force of the low-grade synchronous cone and the high-grade synchronous cone is improved.
Drawings
FIG. 1 is a cross-sectional view of an embodiment of the present invention;
FIG. 2 is a schematic view of the structure within the main tank;
FIG. 3 is a three-dimensional schematic view of a lock mechanism in embodiment 1;
fig. 4 is a three-dimensional schematic view of the lock mechanism in embodiment 2.
Detailed Description
The following is further detailed by way of specific embodiments:
reference numerals in the drawings of the specification include: the device comprises a first shaft 1, a first shaft normally engaged gear 2, a main box 3, an auxiliary box 4, a fifth-sixth gear synchronizer 5, an interlocking shaft 6, a second shaft sixth gear 7, a main shifting fork shaft 8, a second shaft fourth gear 9, a third-fourth gear synchronizer 10, a push rod 11, a second shaft third gear 12, a second shaft second gear 13, a locking chute 14, a second-gear synchronizer 15, a second shaft first gear 16, an arc-shaped groove 17, a second shaft reverse gear 18, a limiting block 19, a limiting groove 20, a second shaft 21, an intermediate shaft 22, a spring 23, an intermediate shaft normally engaged gear 24, an intermediate shaft sixth gear 25, an intermediate shaft fourth gear 26, an intermediate shaft third gear 27, an intermediate shaft second gear 28, an intermediate shaft first gear 29, an idle gear 30, a first gear 31, a reverse shaft 32, a second gear 33, a gear column 34, a power output shaft 35, a sun gear 36, a planet carrier 37, a planet gear 38, a gear 39, a high-low gear synchronizer assembly 40, an auxiliary shifting fork shaft 41 and an auxiliary shifting fork 42.
Example 1:
example 1 is substantially as shown in figures 1 to 3: the helical-tooth double-countershaft twelve-speed transmission shown in FIG. 1 comprises a main box 3 and an auxiliary box 4, wherein the main box 3 and the auxiliary box 4 are directly connected; the main box 3 includes therein a first shaft 1, a second shaft 21, a main fork shaft 8, and a lock mechanism as shown in fig. 3. As shown in fig. 2, the second shaft 21 is coaxial with the first shaft 1, two symmetrical intermediate shafts 22 (only one intermediate shaft 22 is shown in the figure) are arranged on two sides of the second shaft 21, and the intermediate shafts 22 are connected with the main box 3 through tapered roller bearings.
A reverse gear shaft 32 is arranged in the main box 3, and an idler wheel 30 is arranged on the reverse gear shaft 32; a first shaft constant meshing gear 2 is fixedly arranged on the first shaft 1, and a middle shaft constant meshing gear 24, a middle shaft six-gear 25, a middle shaft four-gear 26, a middle shaft three-gear 27, a middle shaft two-gear 28 and a middle shaft first-gear 29 are fixedly arranged on the middle shaft 22 in sequence; a second shaft sixth-gear 7, a second shaft fourth-gear 9, a second shaft third-gear 12, a second shaft second-gear 13, a second shaft first-gear 16 and a second shaft reverse gear 18 are fixedly arranged on the second shaft 21 in sequence; the first shaft constant mesh gear 2 is meshed with a middle shaft constant mesh gear 24, a middle shaft six-gear 25, a middle shaft four-gear 26, a middle shaft three-gear 27, a middle shaft second-gear 28 and a middle shaft first-gear 29 are correspondingly meshed with a second shaft six-gear 7, a second shaft fourth-gear 9, a second shaft third-gear 12, a second shaft second-gear 13 and a second shaft first-gear 16, and the middle shaft first-gear 29 can be meshed with a second shaft reverse gear 18 through an idler gear 30.
A second-gear synchronizer 15 is arranged between a first-gear 16 of the second shaft and a second-gear 13 of the second shaft, a third-fourth-gear synchronizer 10 is arranged between a third-gear 12 of the second shaft and a fourth-gear 9 of the second shaft, and a fifth-sixth-gear synchronizer 5 is arranged on the left side of a sixth-gear 7 of the second shaft (namely between the sixth-gear 7 of the second shaft and the first normally meshed gear 2); the first two-gear synchronizer 15 and the third four-gear synchronizer 10 are double-conical surface synchronizers, and the fifth six-gear synchronizer 5 is a single-conical surface synchronizer; of course, the first-second gear synchronizer 15, the third-fourth gear synchronizer 10 and the fifth-sixth gear synchronizer 5 can adopt three conical surface synchronizers. The main shifting fork shaft 8 is fixed with a main shifting fork for shifting each synchronizer.
The sub-tank 4 is similar to the patent with publication number CN201802841U, and as shown in fig. 1, the sub-tank 4 includes a planetary transmission mechanism, a pneumatic shifting mechanism, a power output shaft 35 and a high-grade synchronous cone base, and the high-grade synchronous cone base is fixed on the power output shaft 35 by a spline. The planetary transmission mechanism comprises a sun gear 36, a planet carrier 37, planet gears 38 and a gear ring 39, wherein the sun gear 36 is fixed at the tail end of the second shaft 21 through splines, namely the part of the second shaft 21 extending into the auxiliary box 4, the planet carrier 37 and the power output shaft 35 are fixed into a rigid whole and are supported on the shell of the auxiliary box 4, the planet gears 38 are sleeved on the planet gear 38 shaft supported on the planet carrier 37 through needle bearings, and the planet gears 38 are meshed with the sun gear 36 and the gear ring 39.
A deep groove ball bearing is sleeved on the power output shaft 35 to abut against the planet carrier 37, a supporting seat is sleeved outside the deep groove ball bearing, and the supporting seat is connected with the gear ring 39 into a whole through a spline; a locking plate fixed on the auxiliary box 4 is arranged outside the supporting seat, a low-gear synchronous cone, a high-low gear synchronizer assembly 40 and a high-grade synchronous cone are sequentially sleeved outside the supporting seat, of course, the planetary transmission mechanism can also be positioned on the left sides of the low-gear synchronous cone, the high-low gear synchronizer assembly 40 and the high-grade synchronous cone, the low-gear synchronous cone and the high-grade synchronous cone exchange positions at the moment, the low-gear synchronous cone is fixed on the locking plate through a spline, the high-grade synchronous cone is fixed on a high-grade synchronous cone base through a spline, and a carbon particle layer is arranged on the friction surface of the low-gear synchronous cone and the high-grade.
The high-low gear synchronizer assembly 40 is controlled by a pneumatic shifting mechanism, the pneumatic shifting mechanism comprises a shifting cylinder and a piston, the shifting cylinder and the auxiliary box 4 are integrally formed, the piston is arranged on an auxiliary shifting fork shaft 41 and located in the shifting cylinder, and an auxiliary shifting fork 42 is arranged on the auxiliary shifting fork shaft 41. An air valve air passage in the pneumatic gear shifting mechanism is controlled and converted through a gear shifting handle, a shifting head on the gear shifting handle is shifted, the air valve air passage is converted, and under the action of compressed air, a piston moves back and forth and drives an auxiliary shifting fork shaft 41 to move, so that a gear sleeve on a high-low gear synchronizer assembly 40 is driven to move, and high-low gear area conversion of an auxiliary box 4 is realized.
As shown in fig. 3, the interlocking device comprises a locking unit and an interlocking shaft 6, wherein the interlocking shaft 6 is slidably arranged in an upper cover of the transmission, the interlocking shaft 6 is perpendicular to three main declutch shift shafts 8, an arc-shaped groove 17 is formed on the circumferential surface of the interlocking shaft 6, the main declutch shift shafts 8 are positioned in the arc-shaped groove 17, a limiting block 19 is integrally formed on the interlocking shaft 6, and a limiting groove 20 is formed on the circumferential surface of each main declutch shift shaft 8; an ejector rod 11 is welded on the auxiliary shifting fork 42, and the ejector rod 11 is parallel to the main shifting fork shaft 8.
The locking unit comprises a spring 23 and two locking chutes 14, the locking chutes 14 are arranged on the ejector rod 11, the length of each locking chute 14 is determined according to the stroke of the corresponding auxiliary shifting fork 42, the spring 23 is arranged at one end of the interlocking shaft 6, one end of the spring 23 is welded with the upper cover of the transmission, and the other end of the spring 23 is welded with one end of the interlocking shaft 6; the other end of the interlocking shaft 6 contacts with the circumferential surface of the carrier rod 11, and the distance between the two locking inclined grooves 14 is smaller than the diameter of the interlocking shaft 6.
The specific implementation process is as follows:
the gear shifting in the main box 3 is controlled by the upper cover assembly and the top cover assembly together, and the structures of the upper cover assembly and the top cover assembly are conventional technologies in the automobile industry, and are not described herein. Under the action of a gear selecting and shifting deflector rod of the top cover assembly, a shifting fork system in the top cover assembly starts to move back and forth to drive a synchronizer between each forward gear and a tooth on a synchronous cone of one gear, and at the moment, a free gear of the gear is combined with a second shaft 21 into a whole, so that the power of the forward gear in the main box 3 is output into the auxiliary box 4. As shown in fig. 2, the details of the power output paths of the respective gears in the main casing 3 are as follows:
first gear: 1 → 24 → 22 → 29 → 16 → 15 → 21; second gear: 1 → 24 → 22 → 28 → 13 → 15 → 21; third gear: 1 → 24 → 22 → 27 → 12 → 10 → 21; fourth gear: 1 → 24 → 22 → 26 → 9 → 10 → 21; fifth gear: 1 → 5 → 21; a sixth gear: 1 → 24 → 22 → 25 → 7 → 5 → 21; reverse gear: 1 → 24 → 22 → 29 → 30 → 18 → 21.
When the transmission is to work in a high-grade area, as shown in fig. 1, a piston in the pneumatic gear shifting mechanism moves and drives an auxiliary shifting fork shaft 41 and an auxiliary shifting fork 42 to move, so that a high-low gear synchronizer assembly 40 is driven to move and is combined with a high-grade synchronous cone, at the moment, the high-grade synchronous cone, a high-grade synchronous cone base, a planet carrier 37, a power output shaft 35, a supporting seat and a gear ring 39 are integrated, and power is output through the power output shaft 35.
When the transmission is to work in a low gear region, as shown in fig. 1, a piston in the pneumatic gear shifting mechanism moves in a reverse direction and drives an auxiliary shifting fork shaft 41 and an auxiliary shifting fork 42 to move in a reverse direction, so that a high-low gear synchronizer assembly 40 is driven to move in a reverse direction and is combined with a low-gear synchronizer cone, the low-gear synchronizer cone, a locking plate, a supporting seat and a gear ring 39 are integrated, the planetary transmission mechanism outputs the gear ratio, and power is output through a sun gear 36, a planet gear 38 and a power output shaft 35.
Wherein, when the high-grade time is hung to auxiliary tank 4, as shown in fig. 3, vice declutch shift shaft 41 is along its axial displacement, thereby drive vice declutch shift 42 and remove and drive ejector pin 11 along its axial displacement, after interlocking axle 6 aligns with locking chute 14, under the spring action of spring 23, interlocking axle 6 removes and slides in locking chute 14, thereby drive stopper 19 card and go into spacing groove 20, main declutch shift shaft 8 action has been avoided, interlocking axle 6 is at the gliding in-process in locking chute 14, the gear shift is accomplished to vice declutch shift 42.
When the auxiliary shifting fork 42 is reset, the auxiliary shifting fork shaft 41 moves reversely along the axial direction thereof, so that the auxiliary shifting fork 42 is driven to move reversely and the ejector rod 11 is driven to move reversely along the axial direction thereof, when the interlocking shaft 6 is transited to the process of circumferential contact with the ejector rod 11 through the locking inclined groove 14, the ejector rod 11 pushes the interlocking shaft 6 to move reversely, so that the limiting block 19 is pulled out from the limiting groove 20, and the main shifting fork shaft 8 can slide.
When the auxiliary box 4 is in a low gear, the moving directions of the auxiliary shifting fork shaft 41, the auxiliary shifting fork 42 and the ejector rod 11 are opposite to the moving direction of the auxiliary box 4 when the auxiliary box 4 is in a high gear, and the other conditions are the same as the moving direction of the auxiliary box 4 when the auxiliary box 4 is in a high gear.
Example 2:
unlike embodiment 1, as shown in fig. 4, the locking unit includes a first rack 31, a second rack 33, and a gear column 34, the first rack 31 is welded to the interlocking shaft 6, the second rack 33 is welded to the carrier rod 11, the gear column 34 is rotatably disposed in the transmission upper cover, and both the first rack 31 and the second rack 33 are engaged with the gear column 34; two opposite limiting grooves 20 are formed in the circumferential surface of the main shifting fork shaft 8, two limiting blocks 19 are integrally formed on the interlocking shaft 6, and the depth of each limiting groove 20 is determined according to the stroke of the auxiliary shifting fork 42.
The specific implementation process is as follows:
different from embodiment 1, as shown in fig. 4, when the auxiliary box 4 is used for hanging high-grade, the auxiliary shifting fork shaft 41 moves along the axial direction thereof, so as to drive the auxiliary shifting fork 42 to move and drive the ejector rod 11 to move along the axial direction thereof, and further drive the second rack 33 to move, the second rack 33 drives the gear post 34 to rotate, so as to drive the first rack 31 to move, and further drive the interlocking shaft 6 to move, the limiting block 19 is clamped in the limiting groove 20, so that the action of the main shifting fork shaft 8 is avoided, and the auxiliary shifting fork 42 completes the gear shifting in the process that the limiting block 19 moves in the limiting groove 20.
When the lower gear is hung after the auxiliary box 4 is reset, the auxiliary shifting fork shaft 41 reversely moves along the axial direction thereof, so that the auxiliary shifting fork 42 is driven to reversely move and the ejector rod 11 is driven to reversely move along the axial direction thereof, and then the second rack 33 is driven to reversely move, the second rack 33 drives the gear post 34 to reversely rotate, so that the first rack 31 is driven to reversely move, and then the interlocking shaft 6 is driven to reversely move, the limiting block 19 is clamped into the limiting groove 20, the action of the main shifting fork shaft 8 is avoided, and the auxiliary shifting fork 42 finishes gear shifting in the process that the limiting block 19 moves in the limiting groove 20.
Example 3:
in the present embodiment, another way to lock the ring gear 39 is provided, as shown in fig. 1, a coupling sleeve is sleeved on the high-low gear synchronizer assembly 40, and the outer peripheral surface of the coupling sleeve is provided with gear teeth through which the coupling sleeve can be engaged with the inner ring of the ring gear 39.
The above are merely examples of the present invention, and common general knowledge of known specific structures and characteristics in the schemes is not described herein. It should be noted that, for those skilled in the art, without departing from the structure of the present invention, several modifications and improvements can be made, which should also be regarded as the protection scope of the present invention, and these will not affect the effect of the implementation of the present invention and the practicability of the patent.
Claims (10)
1. A twelve-gear transmission with helical teeth and double intermediate shafts is characterized in that: the main box comprises a first shaft, a second shaft, a main shifting fork shaft and a locking mechanism, wherein the second shaft is coaxial with the first shaft, two symmetrical intermediate shafts are arranged on two sides of the second shaft, and the main box is of a parallel shaft type transmission structure and comprises six forward gears and one reverse gear; the auxiliary box is internally provided with a planetary transmission structure which comprises a high gear and a low gear; the locking mechanism comprises a locking unit and an interlocking shaft, the interlocking shaft is perpendicular to the main shifting fork shaft, a limiting groove is formed in the circumferential surface of the main shifting fork shaft, a limiting block is arranged on the interlocking shaft, and the locking unit can clamp the limiting block into the limiting groove and pull out the limiting groove.
2. The skewed tooth dual countershaft twelve speed transmission of claim 1 wherein: the main box also comprises an idle wheel, a first shaft constant mesh gear is fixedly arranged on the first shaft, and a middle shaft constant mesh gear, a middle shaft six-gear, a middle shaft four-gear, a middle shaft three-gear, a middle shaft two-gear and a middle shaft one-gear are fixedly arranged on the middle shaft in sequence; a second shaft six-gear, a second shaft four-gear, a second shaft three-gear, a second shaft two-gear, a second shaft first-gear and a second shaft reverse gear are fixedly arranged on the second shaft in sequence; the first shaft constant mesh gear is meshed with the intermediate shaft constant mesh gear, the intermediate shaft six-gear, the intermediate shaft four-gear, the intermediate shaft three-gear, the intermediate shaft second-gear and the intermediate shaft first-gear are correspondingly meshed with the second shaft six-gear, the second shaft four-gear, the second shaft third-gear, the second shaft second-gear and the second shaft first-gear, and the intermediate shaft first-gear can be meshed with the second shaft reverse gear through the idle gear; synchronizers are arranged between the first-gear of the second shaft and the second-gear of the second shaft, between the third-gear of the second shaft and the fourth-gear of the second shaft and on one side of the sixth-gear of the second shaft.
3. The skewed tooth dual countershaft twelve speed transmission of claim 2 wherein: the auxiliary box comprises a planetary transmission mechanism, a pneumatic gear shifting mechanism, a power output shaft and a high-grade synchronous cone base, and the high-grade synchronous cone base is fixed on the power output shaft; the planetary transmission mechanism comprises a sun gear, a planet carrier, a planet gear and a gear ring, a support seat is sleeved on the power output shaft, and the support seat is connected with the gear ring into a whole through a spline; and a low-gear synchronous cone, a high-gear synchronous cone and a high-low gear synchronizer assembly controlled by the pneumatic gear shifting mechanism are arranged outside the supporting seat, and the high-low gear synchronizer assembly comprises a combination sleeve which can be meshed with the gear ring.
4. A skewed tooth dual countershaft twelve speed transmission as claimed in claim 3 wherein: the synchronizer is a three-conical surface synchronizer.
5. The skewed tooth, dual countershaft twelve speed transmission of any one of claims 1 or 4 wherein: the auxiliary box also comprises an auxiliary shifting fork shaft and an auxiliary shifting fork, wherein an ejector rod is fixed on the auxiliary shifting fork and is parallel to the main shifting fork shaft, and the ejector rod is driven by the auxiliary shifting fork shaft.
6. The skewed tooth dual countershaft twelve speed transmission of claim 5 wherein: the locking unit comprises a spring and a locking chute, the locking chute is arranged on the ejector rod, the spring is arranged at one end of the interlocking shaft, the other end of the interlocking shaft can be in contact with the circumferential surface of the ejector rod, or the other end of the interlocking shaft is positioned in the locking chute; the periphery of the main shifting fork shaft is provided with a limiting groove, the interlocking shaft is provided with a limiting block, and the limiting block and the limiting groove are close to one side of the spring.
7. The skewed tooth dual countershaft twelve speed transmission of claim 5 wherein: the locking unit comprises a first rack, a second rack and a gear column, the first rack is fixedly connected with the interlocking shaft, the second rack is fixedly connected with the ejector rod, and the first rack and the second rack are both meshed with the gear column; two opposite limiting grooves are arranged on the circumferential surface of the main shifting fork shaft, and two limiting blocks are arranged on the interlocking shaft.
8. The skewed tooth, dual countershaft twelve speed transmission of any one of claims 6 or 7 wherein: an arc-shaped groove is formed in the circumferential surface of the interlocking shaft, and the main shifting fork shaft is located in the arc-shaped groove.
9. The skewed tooth dual countershaft twelve speed transmission of claim 6 wherein: the quantity of locking chute is two, and the distance between the locking chute is less than the diameter of interlocking axle.
10. A skewed tooth dual countershaft twelve speed transmission as claimed in claim 3 wherein: the friction surfaces of the low-grade synchronous cone and the high-grade synchronous cone are provided with carbon particle layers.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922441706.2U CN211398552U (en) | 2019-12-30 | 2019-12-30 | Twelve-gear transmission with helical teeth and double intermediate shafts |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922441706.2U CN211398552U (en) | 2019-12-30 | 2019-12-30 | Twelve-gear transmission with helical teeth and double intermediate shafts |
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| Publication Number | Publication Date |
|---|---|
| CN211398552U true CN211398552U (en) | 2020-09-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201922441706.2U Active CN211398552U (en) | 2019-12-30 | 2019-12-30 | Twelve-gear transmission with helical teeth and double intermediate shafts |
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| CN (1) | CN211398552U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110939736A (en) * | 2019-12-30 | 2020-03-31 | 綦江齿轮传动有限公司 | Twelve-gear transmission with helical teeth and double intermediate shafts |
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2019
- 2019-12-30 CN CN201922441706.2U patent/CN211398552U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110939736A (en) * | 2019-12-30 | 2020-03-31 | 綦江齿轮传动有限公司 | Twelve-gear transmission with helical teeth and double intermediate shafts |
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| TR01 | Transfer of patent right |
Effective date of registration: 20220401 Address after: 401420 building 103, No. 7, Xichi Avenue, Gunan street, Qijiang District, Chongqing Patentee after: Chongqing Qichi gear Research Institute Co.,Ltd. Address before: 401420 NO.666, Jiefang Road, Qiaohe street, Qinjiang District, Chongqing Patentee before: QIJIANG GEAR TRANSMISSION Co.,Ltd. |