Sixteen-stage gearbox

FIELD: transport.

SUBSTANCE: proposed gearbox incorporates an input and output shafts running in bearings and a lay shaft arranged parallel to the said input and output shafts. The output and lay shafts are furnished with the supports in the gearbox housing intermediate wall. The input shaft rear end is fitted in the output shaft end. The input shaft comprises a reverse drive gear and three forward running gears made integral with the aforesaid shaft. The input shaft supports also dual-direction gear free running thereon and accommodating a two-position coupling. One driven gear runs free on the output shaft end, while two other driven gears are fitted on the output shaft unfixed with a three-position coupling arranged there between. Three drive gears, dual-direction gear and three forward running driven gears in mesh with the input and output shaft gears run on the lay shaft. The reverse gear is fitted unfixed on the lay shaft to engage with the additional reverse gear. The said lay shaft supports two unfixed three-position coupling seating between the lay shaft gears. Similar coupling is fitted on the output shaft end.

EFFECT: reduced metal input, higher efficiency.

2 dwg

 

The invention relates to transport machinery, transmission vehicles.

Known transmission units with speed change gear ratios, containing gears, shafts, bearings, gear used on domestic and foreign cars. (Usachov CENTURIES, Frumkin, A. Car: Analysis of structures, the elements of the calculation. - M.: Mashinostroenie, 1989. - 304 S.).

These units are structurally complex and bulky.

Closest to the offer, such as : KM is a transmission unit of a tractor-700/701.

Eight-three non-axial base KP, supplemented by a two-speed gearbox provides sixteen forward and eight reverse gears. The unit has parallel spaced one above the other input, two intermediate and output shafts. On the input shaft is fixed a drive gear pumps, installed four wheel gear, which is attached to edomim drums friction clutches, and are in constant engagement with the respective gears of the first intermediate shaft, on which are fixed two gear meshed with pinions loosely mounted on the second intermediate shaft, between them is a three-position clutch. On the second intermediate shaft is also fixed on the e gear, meshed with the gear output shaft, between them is a three-position clutch. Leading reverse gear mounted on the first intermediate shaft and driven freely mounted on the second intermediate shaft next to dip the clutch. The intermediate reverse gear is located on a separate axis.

The drawbacks of the transmission unit are low efficiency and high metal consumption, which is caused by the use of friction clutches with a free installation of top gear on the input shaft, increasing their diameter and center of aastana, non-axial location of the shaft excluding the receipt of direct transmission with high efficiency, treharne gearing, reducing efficiency in all gears.

The objective of the invention is to increase the efficiency and reducing the metal of the transmission Assembly.

The technical result is achieved by the presence of direct transmission with coaxial placement of the input and output shafts, Dujardin gear meshing with other gears, reduction center distances between aligned and intermediate shafts.

The achievement of the technical result is ensured by the fact that, such as : a transmission, comprising a housing Assembly holds the input, output and intermediate shafts, a pair of gears forward-reverse, and the poison reverse gears, leading reverse gear meshed with the driven gear via an additional gear mounted on a separate axis on the output shaft, two gears mounted freely between these gears is a three-position clutch, the housing Assembly has an intermediate wall, the rear end of the input shaft is installed in the tip of the output shaft, on which is a three-position clutch, the input shaft is fixed a leading reverse gear and three leading gear forward stroke, the gear dual direction located on it dip clutch installed freely on the intermediate shaft secured three top gear and pinion double direction, freely installed three driven gears the forward stroke and the slave reverse gear, between the loosely mounted gears are two three-position clutch.

Figure 1 shows the kinematic diagram of the three-shaft coaxially KP 16R4 (16 speeds forward and 4 reverse gears), containing 14 gears for speeds forward and 3 gears for reverse gears, 5 couplings gear. In the lower part there are the numbers of pairs of gears forward course (1-7) and the designation of a number of gears reverse - R.

Figure 2 shows the radiation diagram of this control tables of the provisions of the clutch switch on the discrepancies between the different gears front (top) and rear (bottom) of a course. In the upper part of the table marked incorporated into the pair of gears (1-7) or the number of gears reverse (R). On the horizontal scale is given in the logarithmic value of the gear ratio pairs of gears and gear. Extreme horizontal lines correspond to the output shaft, and the average intermediate shaft. Input shaft corresponds t.15 on the upper horizontal left. The greater the inclination of the beam to the right, the greater the gear ratio. The left slope of the beam indicates an accelerating mode of the pair of gears. The tilt of the beam of each pair of gears is constant on any part of the radiation diagram.

In bearings of the housing unit 1 is input 2, output 3 and intermediate 4 shafts. Input 2 and output 3 shafts are coaxial, and the intermediate shaft 4 is parallel to the coaxial shafts and the output shaft 3 and the intermediate shaft 4 also have a bearing in the intermediate wall 5 of the housing unit 1.

The rear end of the input shaft 2 is installed in the tip 6 of the output shaft 3. On the input shaft 2 is fixed or made jointly with the shaft leading reverse gear 7 and the leading gear front turn 8, 9 and 10, and the gear double direction 11 loosely mounted on this shaft. Driven gear 12 is freely mounted on the tip 6 of the output shaft 3. The driven gears 13 and 14 are loosely mounted on the output shaft 3. On premiato the nom shaft 4 fixed wheel gear 15, 16, 17 and gear double direction 18 and freely mounted driven gear front turn 19, 20 and 21, meshed respectively with the gears 14 and 13 of the output shaft, the gear 12 of the tip 6 of the output shaft 3, and gears 11, 10, 9 and 8 of the input shaft 2. Led by the reverse gear 22 loosely mounted on the intermediate shaft 4, meshed with an additional reverse gear 23 mounted on single axis 24 and through it with leading reverse gear 7. Three-position clutch 25 (a) is mounted on the intermediate shaft 4 between the gears 21 and 22, similar to the clutch 26 (B) installed between the gears 19 and 20, a two-position clutch 27 (C) is installed on the crown gear 11. Three-position clutch 28 (D) is located on the tip 6 of the output shaft 3, the three-position clutch 29 (E) is located on the output shaft 3 between the gears 13 and 14.

Work, such as : KP as follows.

The first transmission

Clutches a and E in the right position (P), and the clutch b, C, D - neutral (see figure 2, table. right on vol. 1). Torque (see figure 1) from the input shaft 2 is transmitted by a pair of gears 8-21, clutch 25 (A) on the intermediate shaft 4, a further pair of gears 15-14 and clutch 29 (F) on the output shaft 3. Radiation diagram (see figure 2) this transmission is represented by two beams: beam 1 out of t.15 the left on the top horizontal and the direction is to the right, down to the middle horizontal, further, the beam 7 to 1 on the right side of the horizontal axis.

A second pass

Switchable clutch in neutral position switch off from work a couple of gears 8-21, and the clutch is In the left position - include a couple of gears 9-20. Torque from the input shaft 2 through a pair of gears 9-20 is transmitted by the clutch 26 (b) on the intermediate shaft 4, and further, as in first gear. Radiation diagram this transmission is represented by two rays: 2 and 7 from t.15 to v.2.

Third gear

Return the clutch In neutral position switch off from work a couple of gears 9-20, move the clutch to the left position (L) is included in the job a couple of gears 11-18. The torque is transmitted from the input shaft 2 through a pair of gears 11-18, the clutch switch 27 (C) on the intermediate shaft 4, then, as in the previous transmission. Radiation diagram this transmission is represented by the beams 4 and 7, designed to v.3.

The fourth transfer

Return the clutch in neutral position switch off from work a couple of gears 11-18, move the clutch in the right position (P) is included in the job a couple of gears 10-19. The torque is transmitted from the input shaft 2 through a pair of gears 10-19, the clutch switch 26 (b) on the intermediate shaft 4, then, as in the previous transmission. Radiation diagram this transmission is represented by rays 3 and 7, designed to v.4.

The fifth transmission

Return the clutch In neutral Polo is giving - switch off from work a couple of gears 11-18, move the clutch And in the right position (P) is included in the job a couple of gears 8-21, and the clutch E to the left (L), instead of a pair of gears 15-14 included in the job a couple of gears 16-13. The torque is transmitted from the input shaft 2 to the intermediate shaft 4, as in first gear, then through a couple of gears 16-13 and clutch 29 (F) on the output shaft 3. Radiation diagram this transmission is represented by beams 1 and 6 aimed to V.5.

The sixth transmission

Return the clutch in neutral position switch off from work a couple of gears 8-21, move the clutch to the left position (L) is included in the job a couple of gears 9-20. The torque is transmitted to the intermediate shaft 4, as on the second pass, then, as on a previous pass. Radiation diagram this transmission is represented by rays 2 and 6 aimed to V.6.

The seventh transmission

Return the clutch In neutral position switch off from work a couple of gears 9-20, move the clutch to the left position (L) is included in the job a couple of gears 11-18. The torque is transmitted to the intermediate shaft 4 as in third gear, then as in the previous two passes. Radiation diagram this transmission is represented by the beams 4 and 6 are directed to v.7.

The eighth transmission

Return the clutch in neutral position switch off from work a couple of gears 11-18, AC is seem the clutch in the right position (P) - included in the job a couple of gears 10-19. The torque is transmitted to the intermediate shaft 4, as in fourth gear, then, as in the three previous transmission. Radiation diagram this transmission is represented by rays 3 and 6 aimed to T.8.

The ninth transmission

Return the clutch In neutral position switch off from work a couple of gears 10-19, move the clutch And in the right position (P) is included in the gear 8-21, clutch in neutral position switch off from work a couple of gears 16-13, and the sleeve D in the right position (P) is included in the job a couple of gears 17-12. The torque is transmitted to the intermediate shaft 4, as at the first and fifth gears, then through a couple of gears 17-12 and the clutch 28 (D) on the output shaft 3. Radiation diagram this transmission is represented by rays 1 and 5 aimed to v.9.

The tenth transmission

Return the clutch in neutral position switch off from work a couple of gears 8-21, move the clutch to the left position (L) is included in the gear 9-20. The torque is transmitted to the intermediate shaft 4, as in the second and sixth gear, then, as on a previous pass. Radiation diagram this transmission is represented by rays 2 and 5 aimed to V.10.

The eleventh transmission

Return the clutch In neutral position switch off from work a couple of gears 9-20, move the clutch to the left position (the) - included in the job a couple of gears 11-18. The torque is transmitted to the intermediate shaft 4, as in the third and seventh gears, then, as in the previous two passes. Radiation diagram this transmission is represented by the beams 4 and 5 aimed to t.

The twelfth transmission

Return the clutch in neutral position switch off from work a couple of gears 11-18, move the clutch in the right position (P) is included in the gear 10-19. The torque is transmitted to the intermediate shaft 4, as in the fourth and eighth transmission, hereinafter referred to as on the three previous transmission. Radiation diagram this transmission is represented by rays 3 and 5 aimed to vol.12.

The thirteenth transmission

Return the clutch In neutral position switch off from work a couple of gears 10-19, move the clutch And in the right position (P) is included in the gear 8-21, the coupling D to the left (L) - instead of a pair of gears 17-12 include a couple of gears 18-11. A pair of gears 11-18 double direction; on the third, seventh and eleventh gears this pair worked from the input shaft 2 to the intermediate shaft 4, on the 13th the transfer and then this pair works in the other direction from the intermediate shaft 4 through a pair of gears, then the coupling D to the tip 6 of the output shaft 3.

The torque is transmitted from the input shaft 2 through a pair of gears 8-21, the clutch switch 25 (a) temporarily the output shaft 4, then through a couple of gears 18-11 and clutch 28 (D) on the output shaft. Radiation diagram this transmission is represented by rays 1 and 4 aimed to v.13.

The fourteenth transmission

Return the clutch in neutral position switch off from work a couple of gears 8-21, move the clutch to the left position (L) is included in the gear 9-20. The torque is transmitted to the intermediate shaft 4, as for the second, sixth and tenth gears, then, as on a previous pass. Radiation diagram this transmission is represented by rays 2 and 4 aimed to t.

The fifteenth transmission - direct

Return the clutch In neutral position switch off from work a couple of gears 9-20, move the clutch to the left position (L). The torque is transmitted from the input shaft 2 through the gear 10, the clutch switch 27 to the gear 11, further coupling 28 to the output shaft 3. Radiation diagram this transfer presents t.15.

Sixteenth transfer - accelerating

Return the clutch in neutral position, move the clutch in the right position (P) is included in the work of a pair of gears 10-19 and 18-11. The torque is transmitted from the input shaft 2 through a pair of gears 10-19, the clutch switch 26 (b) on the intermediate shaft 4, a further pair of gears 18-11 and the clutch 28 (D) on the output shaft 3. Radiation diagram this transmission is represented by rays 3 and 4 aimed to t.16..

Transfer the ass is included in rate when moving the clutch And to the left position, which connects the gear 22 with the intermediate shaft 4. The provisions of the clutches D, E (see tables).

The first back - 1R

Clutch And is in the left position, the clutch b, C and D is in neutral and the clutch is in the right position (see figure 2, tablspace under .1R). Torque from the input shaft 2 is transmitted through the gears 7-23-22 clutch And the intermediate shaft 4 and the clutch E and the pair of gears 15-14 on the output shaft 3, which rotates in the direction opposite to rotation of the input shaft 2.

Radiation diagram this transmission is represented by two rays: ray R from t.15 on the top left horizontal right down to the middle horizontal line, then a gentle beam 7 is also right down to .1R on the lower horizontal line.

The second back - 2R

Switchable clutch E in the left position. To the intermediate shaft 4 torque is transmitted, as in the previous transmission, then through a couple of gears 16-13 and the clutch 29 to the output shaft 3. Radiation diagram of this transfer correspond to the rays R and 6.

The third back - 3R

Switchable clutch in neutral position and the clutch D is in the right position. To the intermediate shaft 4 torque is transmitted, as in the previous transmission, then through a couple of gears 17-12 and clutch 28 to the output shaft 3. Radiation diagram of this transfer correspond to the rays R and 5.

Fourth reverse - 4R

Switchable coupling D to the left position. Until about itocnode shaft 4 torque is transmitted, as on a previous pass, then through gear 18-11 and clutch 28 to the output shaft 3. Radiation diagram of this transfer correspond to the rays R and 4.

Such as : transmission, comprising a housing Assembly holds the input, output and intermediate shafts, a pair of gears forward-reverse, and a number of gears reverse, leading reverse gear meshed with the driven gear via an additional gear mounted on a separate axis on the output shaft, two gears mounted freely between these gears is a three-position clutch, wherein the housing Assembly has an intermediate wall, the rear end of the input shaft is installed in the tip of the output shaft, on which is a three-position clutch, the input shaft is fixed a leading reverse gear and three leading gear forward course, gear double direction with located on it dip clutch installed freely on the intermediate shaft secured three top gear and pinion double direction, freely installed three driven gears forward-reverse, and led the reverse gear, between the loosely mounted gears are two three-position clutch.



 

Same patents:

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2 dwg

FIELD: mechanic.

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FIELD: transport engineering.

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FIELD: transport.

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Planetary gearbox // 2324850

FIELD: transportation, trackless surface vehicles.

SUBSTANCE: invention pertains to the field of motor transport engineering and relates to staggered planetary gear box. The automatic hydro mechanical gear box consists of casing (1), input link (3), output link (4) and planetary reduction gear. In the planetary reduction gear, there are three frictional clutches and four friction brakes. The first planetary gear set consists of central gear (5), drive (6) for satellites and crown gear (7). The second planetary gear set consists of central gear (8), drive (9) for satellites and crown gear (10). The third planetary gear set consists of central gear (11), drive (12) for satellites and crown gear (13). The input link (3) is joined to rigidly interconnected drive (6) and the central gear (8). The crown gear (13) is connected to the output link (4) of the gear box. Drive (9) is connected to the control frictional clutch (15) through drive (6), which is rigidly connected to the central gear (8). Crown gear (10) is connected through the control frictional clutch (16) to drive (12), which is rigidly fixed to the central gear (5). Frictional brakes (17) joins the crown gear (7) to the casing (1) of the gear box. Frictional brakes (18) connect interconnected drive (9) and central gear (11) to the casing (1) of the gear box. Frictional brakes (19) connects the crown gear (10) to the casing (1) of the gear box. Frictional brakes (20) connects interconnected drive (12) and the central gear (5) to the casing (1) of the gearbox. This allows for enhancement of dynamic properties and broadening of the range of transmission ratios.

EFFECT: enhancement of dynamic properties and broadening of the range of transmission ratios.

5 cl, 6 dwg

FIELD: transport engineering.

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2 dwg

FIELD: transport engineering.

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2 dwg

FIELD: transport engineering.

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EFFECT: enlarged operating capabilities of vehicle, reduced metal usage of set.

2 dwg

Gearbox // 2319623

FIELD: automotive industry.

SUBSTANCE: gearbox is designed for mounting onto all-wheel-drive trucks. Gearbox case 1 accommodates drive shaft 2, countershaft 3, driven shaft 4, reverse idler gear 5, planetary gear train 6 and interaxle differential 7 are installed on one axle and have common carrier 8. Sun gear of planetary gear train 10 is installed on driven shaft 4. Fitted on drive shaft 2 are double-acting clutches 11 and 12, four rotating gears 13, 14, 15 and 16 and two fixed gears 17 and 18. Fitted on countershaft 3 are double-acting clutch 19, two rotating gears 20 and 21, and four gears 22, 23, 24 and 25 which are fixed. Double-acting clutch 26 and two rotating gears 27 and 28 are installed on shaft 3. Planet pinions 29 of planetary gear train and planet pinions 30 of interaxle differential are arranged on one axle. Ring gear 9 of planetary gear train can alternately engage with toothed rim 31 secured on case 1 and toothed rim 32 on carrier 8. Ring gear 33 of planetary mechanism of interaxle differential is in constant meshing with toothed rim 34 which is secured on shaft 35 of axle drive and can be meshed with toothed rim 36 secured on carrier 8. Sun gear of planetary mechanism of interaxle differential is installed on axle drive shaft 38.

EFFECT: reduced power losses in transmission, noise level in operation, increased number of speeds with optimum kinematic parameters.

2 cl, 2 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to stepless mechanical transmission on base of inertia impulse transmission. Proposed transmission consists of input shaft 1 rigidly connected with housing of impulse mechanism 2 mechanically coupling with intermediate shaft 3 in which two overrunning mechanisms are installed, main mechanism 4 and output mechanism 5. Outer race 6 of main overrunning mechanism is connected with transmission case by means of cam clutch 7. Inner clutch member 8 of one of cam clutches is rigidly connected with housing of impulse mechanism. Clutch member 9 of second clutch is rigidly connected with flywheel 10 of output shaft. Outer race 11 of one of cam clutches is arranged on intermediate shaft between housing of impulse mechanism and main overrunning mechanism. Outer clutch member 12 of second cam clutch is installed on intermediate shaft between flywheel of output shaft and main overrunning mechanism. Outer clutch member 12 is rigidly connected with cam clutch 7 of main overrunning mechanism.

EFFECT: provision of transmission of torque from flywheel of output shaft to input shaft and vice versa.

3 dwg

Planetary gearbox // 2318144

FIELD: mechanical engineering; transmissions of vehicles.

SUBSTANCE: design peculiarity of proposed planetary gearbox is that planetary-pin tooth trains featuring multipair meshing are used as planetary trains 4-8 in gearbox, heaving common input eccentric shaft 2 and common carrier. Central wheels 9 of each planetary-pin tooth train engage with brakes 17-21. Common carrier is coupled with output 3.

EFFECT: increased load carrying capacity in combination with compactness.

4 cl, 2 dwg

Gearbox // 2313709

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: proposed gearbox contains constant-mesh gear cluster as main speed unit and planetary mechanism for additional reduction with multiplication of main low speed. All driven gears of cluster and planetary mechanism are fitted on gearbox output shaft, and driving member of planetary mechanism-sun or ring gear - is nondetachably rigidly connected with driven gear of main low speed.

EFFECT: simplified kinematic of transmission, reduced mechanical losses.

5 cl, 4 dwg

FIELD: transport engineering; tractor transmissions.

SUBSTANCE: invention proposed two design versions of compound transmission. According to first design version, both brakes and lock-up clutch of auxiliary three-speed planetary gearbox are arranged in one housing. One of brakes and lock-up clutch are fitted on common hub installed on shaft of one of sun gears. Drum of lock-up clutch and carrier are fitted on input member - input shaft of auxiliary gearbox. Output member is hub of ring gear which is connected with input shaft of main gearbox. According to second design version of compound transmission both brakes and lock-up clutch and of auxiliary gearbox are arranged in one housing. One of brake and lock-up clutch are fitted on common hub installed on shaft of one of sun gears. Drum of lock-up and carrier are installed on output member - output shaft of auxiliary gearbox which is connected with input shaft of main gearbox. Hub of ring gear is input member.

EFFECT: provision of compound transmission with reduced overall dimensions and metal usage, mainly in auxiliary gearbox.

10 cl, 4 dwg

FIELD: transport engineering; tractors.

SUBSTANCE: invention relates to hydraulically operated friction clutches. Proposed friction clutch contains hub secured on shaft of gearbox, hydraulic cylinder with radial projections made on hub, piston with pressure disk, thrust disk, inner drum made integral with driven gear and connected by gear joint with driving disks, driven disks connected with outer drum, ring groove made on inner surface of outer drum, and lockring. Novelty is that outer drum and thrust disk are made in form of common part, outer drum is provided with longitudinal projections, with outer projections of driven disks fitted in slots between longitudinal projections. Ends of projections of outer drum are installed between radial projections of hydraulic cylinder, and lockring is arranged in ring channel formed by ring grooves made on inner surface of outer drum and on outer surface of hydraulic cylinder.

EFFECT: reduced wear of disks, increased transmitted power and improved repairability of clutch.

2 dwg

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