CN218377543U

CN218377543U - Compact twelve-gear gearbox

Info

Publication number: CN218377543U
Application number: CN202222341926.XU
Authority: CN
Inventors: 陆学利; 汤结贵; 张海波; 沈亚军
Original assignee: Chongqing Qichi Gear Research Institute Co ltd
Current assignee: Chongqing Qichi Gear Research Institute Co ltd
Priority date: 2022-08-31
Filing date: 2022-08-31
Publication date: 2023-01-24
Anticipated expiration: 2032-08-31

Abstract

The utility model relates to a gearbox field discloses a twelve keep off gearbox of compact, including main tank, auxiliary tank, the main tank includes the input shaft, the main shaft, the stopper assembly, the oil pump unit, and the input shaft is coaxial with the main shaft, and the input shaft both sides are equipped with the jackshaft of two symmetries and the reverse gear axle of two symmetries, and stopper assembly, oil pump unit set up respectively at two jackshaft tip, and the main tank is parallel shaft transmission structure, is equipped with 2 fender positions on the input shaft, is equipped with 3 on the main shaft and gos forward fender and 1 reverse gear, and the auxiliary tank is planetary gear transmission structure, and the auxiliary tank includes 2 fender positions. The utility model discloses retrench gearbox gear structure, promote the security that the truck went, promote the flexibility of reversing gear.

Description

Compact twelve-gear gearbox

Technical Field

The utility model relates to a gearbox field, concretely relates to twelve fender gearboxes of compact.

Background

The dead weight and the load of the truck are both large, so that low gear ratio amplification torque is required during starting and accelerating, and dozens of gears are required for reducing the torque at high speed.

At present, the domestic twelve-gear heavy truck gearbox with a secondary box mostly adopts a 6 x 2 structure, and comprises a main box and a secondary box, wherein the main box comprises an input shaft, a main shaft and two intermediate shafts, the input shaft is provided with 1 gear, the main shaft is provided with 6 forward gears and 1 reverse gear, the secondary box comprises 2 gears, and 6 x 2, namely 12 groups of forward gears and 1 x 2, namely 2 groups of reverse gears are formed, and the structure has the following defects:

1. the gear sets are multiple, heavy, occupy space and are inconvenient to maintain.

2. The gears used when the heavy truck backs are related to the ground gradient and whether the heavy truck is in idle load or not, and only 2 reverse gears cannot be used.

3. Due to the fact that the self weight and the load of the truck are large, when the truck is braked, the gearbox responds slowly, and the braking distance is long.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a twelve fender gearboxes of compact to retrench gearbox gear structure, promote the security that the truck went, promote the flexibility of reversing gear.

In order to achieve the above purpose, the utility model adopts the following technical scheme: the utility model provides a compact twelve keep off gearbox, includes main tank, auxiliary tank, and the main tank includes input shaft, main shaft, stopper assembly, oil pump unit, and the input shaft is coaxial with the main shaft, and the input shaft both sides are equipped with the jackshaft of two symmetries and the reverse gear axle of two symmetries, and stopper assembly, oil pump unit set up respectively at two jackshaft tip, and the main tank is parallel shaft transmission structure, is equipped with 2 fender positions on the input shaft, is equipped with 3 on the main shaft and advances to keep off and 1 reverse gear, and the auxiliary tank is planetary gear transmission structure, and the auxiliary tank includes 2 fender positions.

The beneficial effects of the scheme are as follows:

1. two gears on the input shaft double the number of gear sets in the main box, so that the gearbox forms 2 x 3 x 2, namely 12 forward gears, and 2 x 2, namely 4 reverse gears. Compare in 6 the gearbox structure of 2, keep off under the same condition of gear group number, this scheme main tank has reduced the fender position, has simplified the gearbox structure, the maintenance of being convenient for.

2.4 reverse gears can adapt to the reversing condition of different ground slopes and under no-load and full load.

3. The intermediate shaft is provided with gears corresponding to the gears, the number of the gears is reduced, and the length of the intermediate shaft can also be reduced, so that a reserved space is reserved for the arrangement of a brake assembly and an oil pump unit.

4. Compared with the brake of the brake pad on the tire, the brake assembly directly brakes the end part of the intermediate shaft, is close to a power output position (engine) and is matched with the brake pad on the tire, so that the braking time is shorter, the effect is better, and the safety is higher.

5. The jackshaft is through rotatory, for the oil pump provides power, and the oil pump can make lubricating oil flow into brake assembly and cool down, also can make the lubricating oil flow to other power transmission unit and lubricate.

Preferably, as an improvement, the auxiliary box comprises a planetary unit, the planetary unit comprises a planet carrier, a planet shaft, a sun gear, a gear ring and a plurality of planet gears, the sun gear rotates synchronously with the main shaft, the planet shaft is arranged on the planet carrier, the planet gears are sleeved on the planet shaft, the gear ring is sleeved on all the planet gears simultaneously, the sun gear, the planet gears and the gear ring are meshed in sequence, one side, close to the planet carrier, of the sun gear protrudes relative to the planet gears, an annular groove is formed in the protruding part of the sun gear, and a thrust ring is sleeved on the groove.

So set up, the main shaft passes to the sun gear with power, and the sun gear passes to the planet wheel with power, and the planet wheel drives the planet carrier rotation through the planet axle simultaneously, and then with power take off, the operation of drive truck. Generally, in order to reduce the abrasion between the planet wheel and the planet carrier, a gasket is usually arranged between the planet wheel and the planet carrier, and the gasket is sleeved on a planet shaft to generate friction with the planet wheel and the planet carrier simultaneously; in the scheme, the thrust ring is sleeved on the sun gear to generate the effect of reducing abrasion, the thrust ring is supported on the groove and only rubs with the planet gear under the driving of the sun gear, abrasion cannot be generated between the thrust ring and the planet carrier, and the service life of the planet carrier is longer.

Preferably, as a refinement, the intermediate shaft includes a low-gear intermediate gear and a reverse-gear intermediate gear which are integrally formed.

So set up, use low gear intermediate gear when 1 keeps off, 2 keep off, use reverse gear intermediate gear when reversing gear, the main shaft rotational speed under the three kinds of circumstances is lower, consequently low gear intermediate gear, reverse gear intermediate gear's radius is less, if directly fix on the jackshaft through the cylindric lock, gear thickness is too thin, damages easily, and low gear intermediate gear, reverse gear intermediate gear and jackshaft integrated into one piece have strengthened the intensity of low gear intermediate gear, reverse gear intermediate gear, have improved the durability.

Preferably, as an improvement, an odometer induction coil is arranged on the planet carrier. So set up, power passes through the planet carrier and exports the truck wheel, compares in the setting of odometer induction coil on the input shaft, and the odometer induction coil sets up on the planet carrier more closely apart from the wheel, and through the rotatory number of turns of record planet carrier, the mileage of reacing is more accurate.

Preferably, as a refinement, the step differences of adjacent groups of the 12 groups of forward gears are equal. By means of the arrangement, the gear ratio between the gears is adjusted, so that the gear difference of adjacent groups is equal, and further the gear shifting is smoother; the rotating speed of the input shaft is ensured to be within the range of saving the most fuel, and the fuel economy is better.

Drawings

FIG. 1 is a sectional view of an embodiment;

FIG. 2 is a schematic illustration in plan of a reverse gear shaft of the embodiment;

FIG. 3 is a schematic plan view of a fork unit according to an embodiment.

Detailed Description

The following is further detailed by way of specific embodiments:

reference numerals in the drawings of the specification include: <xnotran> 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33, 34, 35, 36, 37, 38. </xnotran>

Examples

The examples are substantially as shown in FIGS. 1-3: a compact twelve-gear transmission comprises a main box and an auxiliary box. The main box comprises a front shell 1, a middle shell 2, an input shaft 4, an intermediate shaft 5, a main shaft 6, a brake assembly 18, an oil pump unit 19, a synchronizer, a shifting fork unit and a TCU (transmission control unit), the main box is of a parallel shaft transmission structure, 2 gears are arranged on the input shaft 4, and 3 forward gears and 1 reverse gear are arranged on the main shaft 6; the auxiliary box comprises a rear shell 3, a gear shifting unit, an odometer induction coil 31 and a planetary unit, wherein the planetary unit comprises a planet carrier 7, a planet shaft 32, a sun gear 21, a gear ring 34 and three planet gears 33, the auxiliary box is of a planetary gear transmission structure, and the auxiliary box comprises 2 gears to form 2 × 3 × 2, namely 12 groups of forward gears, and 2 × 2, namely 4 groups of reverse gears.

Preceding shell 1, mesochite 2, backshell 3 connect gradually through the bolt, and TCU sets up in the master tank, and TCU is connected with oil pump unit 19, shift fork unit and stopper assembly 18 electricity.

As shown in fig. 1, the input shaft 4, the main shaft 6 and the sun gear 21 are coaxial, the left end of the main shaft 6 is rotatably connected with the input shaft 4 through a thrust bearing, the right end of the main shaft 6 is provided with a transition gear sleeve 35, the transition gear sleeve 35 enables the main shaft 6 and the sun gear 21 to synchronously rotate through splines, the two intermediate shafts 5 are symmetrically arranged on the upper side and the lower side of the input shaft 4, a reverse gear shaft 22 is arranged between each of the two intermediate shafts 5 and the input shaft 4, the brake assembly 18 is arranged at the left end of one intermediate shaft 5, and the oil pump unit 19 is arranged at the left end of the other intermediate shaft 5.

The oil pump unit 19 includes an oil pump and an oil pipe through which the oil pump delivers lubricating oil to the brake assembly 18 and other power transmission units.

The input shaft 4 is supported on the front shell 1 through a spherical bearing, an input shaft gear 8 and a three-gear 14 are arranged on the input shaft 4, the input shaft gear 8 is in sliding connection with the input shaft 4 through a spline and performs axial limiting through a space ring, and the three-gear 14 is supported at the right end of the input shaft 4 through a thrust bearing.

Jackshaft 5 supports in the front on shell 1 and mesochite 2 through two taper bearing, jackshaft 5 goes up from a left side to the right side and is equipped with first intermediate gear 9 in proper order, second intermediate gear 10, third intermediate gear 11, low gear intermediate gear 12 and reverse gear intermediate gear 13, low gear intermediate gear 12, reverse gear intermediate gear 13 and jackshaft 5 integrated into one piece, first intermediate gear 9, second intermediate gear 10 and third intermediate gear 11 pass through spline and jackshaft 5 sliding connection, it is spacing to carry out the axial through the spacer.

A first gear 16, a second gear 15 and a reverse gear are sequentially arranged on the main shaft 6 from left to right, the first gear 16, the second gear 15 and the reverse gear are in sliding connection with the main shaft 6 through splines, and axial limiting is carried out through a space ring.

As shown in fig. 2, both ends of the reverse shaft 22 are respectively connected to the front case 1 and the middle case 2 by bolts. The reverse gear shaft 22 is provided with an idle gear 23, and the idle gear 23 is rotatably provided on the reverse gear shaft 22 through a needle bearing.

The input shaft gear 8 is meshed with the first intermediate gear 9, the third gear 14 is meshed with the second intermediate gear 10, the first gear 16 is meshed with the third intermediate gear 11, the second gear 15 is meshed with the low gear intermediate gear 12, the reverse gear is meshed with the idle gear 23, the idle gear 23 is meshed with the reverse gear intermediate gear 13, and the gear ratio between the gears is controlled so that the step difference of adjacent gears of 12 forward gears is 1.3.

As shown in fig. 1, the planet carrier 7 is connected to the middle casing 2 through a roller bearing at the left end and to the rear casing 3 through a ball bearing at the right end. Sun gear 21, planet wheel 33, ring gear 34 mesh in proper order, planet axle 32 sets up on planet carrier 7 with the interference, planet wheel 33 passes through needle bearing and supports on planet axle 32, ring gear 34 overlaps simultaneously on three planet wheel 33, sun gear 21 passes power to planet wheel 33, planet wheel 33 revolves round sun gear 21 under the common restraint of ring gear 34 and sun gear 21, planet wheel 33 and sun gear 21 reverse rotation, sun gear 21 is close to planet carrier 7 one side and is equipped with annular recess for planet wheel 33 protrusion, be equipped with the thrust ring on the recess, odometer induction coil 31 is connected with planet carrier 7 through the bolt.

The gear shifting unit comprises a low-gear cone hub 27, a high-gear cone hub 28 and a grounding plate 26, wherein the low-gear cone hub 27 is connected with the grounding plate 26 through a spline, and the auxiliary box grounding plate 26 is fixed with the middle shell 2 through a bolt; the high range cone hub 28 is connected to the carrier 7 by splines.

The synchronizers include a range synchronizer 20, a first synchronizer 24, a second synchronizer 25, and a third synchronizer 29, which shift gears between gears or between a high-range cone hub 28 and a low-range cone hub 27. The gear shifting synchronizer 20 is connected with the input shaft 4 in a sliding mode through a spline, and shifts gears between the shaft gear 8 and the third gear 14; the first synchronizer 24 and the second synchronizer 25 are connected with the main shaft 6 in a sliding mode through splines, the first synchronizer 24 switches gears between the third gear 14 and the second gear 15 at the left end of the main shaft 6, and the second synchronizer 25 switches gears between the second gear 15 and the reverse gear 17; the third synchronizer 29 is slidably connected to the transition sleeve 35 by a spline, and the third synchronizer 29 shifts gears between the low-gear hub and the high-gear hub.

As shown in fig. 3, the shifting fork unit includes a shifting fork shaft 37 and a second cylinder 36, the model of the second cylinder 36 is V1656239, a piston 38 is arranged in the second cylinder 36, the piston 38 is connected with the end of the shifting fork shaft 37, and the piston 38 drives the shifting fork shaft 37 to move, so as to drive the synchronizer to switch gears.

The specific implementation steps are as follows:

the TCU sends a braking instruction to the brake assembly 18, and the brake assembly 18 stops the rotation of the intermediate shaft 5, so that the whole gearbox stops rotating; meanwhile, the TCU sends a command to the oil pump unit 19, and the oil pump unit 19 conveys lubricating oil to the brake assembly 18 for cooling and conveys the lubricating oil to other power transmission units for lubrication. The TCU sends a gear shifting command to the shifting fork unit, and then drives the synchronizer to switch gears.

The power output route in the main box is as follows:

1-11 forward gears: input shaft 4 → intermediate shaft 5 → main shaft 6;

12 forward gear: input shaft 4 → main shaft 6;

reverse gear: input shaft 4 → intermediate shaft 5 → reverse shaft 22 → main shaft 6.

The power output route in the auxiliary box is as follows:

low, ring gear 34 is fixed with ground plate 26: main shaft 6 → sun gear 21 → planet gear 33 → planet carrier 7;

high gear, main shaft 6, sun gear 21 and planet carrier 7 rotate synchronously: main shaft 6 → carrier 7.

The odometer induction coil records the rotating number of turns of the planet carrier, and the obtained driving mileage is more accurate.

The above description is only an example of the present invention, and the common general knowledge of the known technical solutions and/or characteristics is not described herein. It should be noted that, for those skilled in the art, without departing from the technical solution 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. The scope of the claims of the present application shall be defined by the claims, and the description of the embodiments and the like in the specification shall be used to explain the contents of the claims.

Claims

1. A compact twelve-gear transmission comprises a main box and an auxiliary box, and is characterized in that: the main box comprises an input shaft, a main shaft, a brake assembly and an oil pump unit, wherein the input shaft is coaxial with the main shaft, two symmetrical intermediate shafts and two symmetrical reverse gear shafts are arranged on two sides of the input shaft, the brake assembly and the oil pump unit are respectively arranged at the end parts of the two intermediate shafts, the main box is of a parallel shaft transmission structure, 2 gears are arranged on the input shaft, 3 forward gears and 1 reverse gear are arranged on the main shaft, the auxiliary box is of a planetary gear transmission structure, and the auxiliary box comprises 2 gears.

2. The compact twelve speed transmission of claim 1, wherein: the auxiliary box comprises a planet unit, the planet unit comprises a planet carrier, a planet shaft, a sun wheel, a gear ring and a plurality of planet wheels, the sun wheel and a main shaft synchronously rotate, the planet shaft is arranged on the planet carrier, the planet wheels are sleeved on the planet shaft, the gear ring is sleeved on all the planet wheels at the same time, the sun wheel, the planet wheels and the gear ring are sequentially meshed, one side of the sun wheel, which is close to the planet carrier, protrudes relative to the planet wheels, an annular groove is formed in the protruding portion of the sun wheel, and a thrust ring is sleeved on the groove.

3. A compact twelve speed transmission according to claim 1, wherein: the intermediate shaft comprises a low-gear intermediate gear and a reverse-gear intermediate gear which are integrally formed.

4. A compact twelve speed transmission according to claim 2, wherein: and the planet carrier is provided with an odometer induction coil.

5. A compact twelve speed transmission according to claim 1, wherein: the step differences of adjacent groups of forward gears of each group are equal.