Sixteen-speed shaft-planetary gearbox

FIELD: transport.

SUBSTANCE: gearshift clutch and toothed rim with internal and external gearing, controlled by one sliding bar, allow operating planetary mechanism in three operating conditions. The first operating condition is direct transmission, the second operating condition means reduction gear with maximum gear ratio and stopped epicyclical wheel and the third operating condition means reduction gear with output shaft reverse rotation and stopped pinion frame.

EFFECT: better operating performances due to increased number of forward speeds, increased efficiency.

2 dwg

 

The invention relates to the transport industry, in particular to transmission vehicles.

Known transmission units with speed change gear ratios, containing gears, shafts, bearings, gear used on domestic and foreign vehicles (cars: Design, construction and calculation. Transmission. Ed. Aigrettes. Mn.: Enter. HQ., 1985. - 240 S.).

These units are structurally complex, massive.

Closest to the proposed transmission (gearbox) is KP for patent RU 2053138 (bull. N 3 from 27.01.1996).

The transmission includes a housing unit in which there are three coaxial gearbox with four pairs vzaimozachetnykh gear external gear, the gear on the primary and secondary shafts installed freely between them are three clutch gear, the gear on the intermediate shaft joint in the two blocks between the blocks gears installed another clutch switch, interconnected with a fork switch with the clutch located freely on the fixed gear coaxially of the shaft, the output gear is a simple three planetary gear with the planet carrier, the satellites, the sun gear and the epicycle wheel, primary, secondary shaft of the gearbox, the output in the l carrier and output shaft Assembly are aligned, case epicycle wheel, an output shaft carrier and output shaft Assembly are adjacent sprockets on the ring gear of the output shaft Assembly is installed clutch switch.

Described KP simpler model structures of the transmission units given in the book, provides a sufficient range of gear ratios (the ratio of the gear ratio in a lower gear to a higher), but has limited performance capabilities at low speeds due to the large interval between the first and second gears and reduce the efficiency of the unit during operation of the planetary mechanism in summing mode, especially when a significant transfer numbers (first gear and reverse gear).

The problem to which the invention is directed, is to expand the operational capabilities of the vehicle.

The problem is solved by increasing the number of gears as the front moves in with fourteen to sixteen, and reverse with one transfer up to eight, uniform transmission range, to avoid the operation of the planetary mechanism in summing mode with low efficiency.

This technical result is achieved by the fact that, such as : valvoplasty transmission includes a housing in which is parallel to the shaft of the x freely installed four pairs of meshed gears, external gears, gear on the intermediate shaft combined into two blocks, between the pairs of gears are clutch gear, average clutch double, consisting of two protivoperegruzochnyh one-way clutch switch installed on the gears and related plug switch, the output shaft is fixed sun gear of the simple three-tier planetary mechanism, barrel epicycle wheel, shaft carrier and output shaft are adjacent sprockets on the ring gear output shaft mounted three-position clutch switch, a sun gear mounted on the secondary shaft, coaxially to the primary shaft, the housing epicycle wheel tubular shaft connected to the gear ring, gear shaft drove off, the clutch switch on the gear output shaft has three internal gear on the slide clutch switch is rigidly fixed ring gear with internal and external links, external toothing of which is connected with the three-position ring gear housing Assembly opposite the toothed crowns were taken and body epicycle wheel.

The planetary mechanism (PM) gearbox prototype provides two modes: one in which torque acts on two elements: a sun gear and drove, and snimalsa third link - epicycle wheel; and the second, in which two link PM closed between them, PM is blocked and is working with the ratio U(bh)=1. The number of transmission units is equal to twice the number of gears helical gear minus one - fifteen gears: fourteen speeds forward and one reverse. Distribution transmission range is not optimal - the intervals between transmissions of increase in the area of the lower gear, large gear numbers dramatically decreases the efficiency of the unit. Variant selection of speeds of rotation of the leading elements in which the output link will be fixed - that is, the efficiency of the CP in this case equal to zero.

The proposed solution allows you to implement three modes of operation PM: Ubah=K+1; U(bh)=1; Uhab=-K. the Number of transmission units equal to three times the number of gears helical gear - 24 transmission: 16 speeds forward and 8 reverse gears. Distribution transmission range preferably are provided with equal intervals between transmissions, excluded transmission in summarizing the operation mode PM with low efficiency.

Figure 1 shows the kinematic diagram of the gearbox, at the bottom of these symbols of pairs of gears (1-4); figure 2 - radial chart and table position clutch switch at different speeds forward.

On axes radial diag is Amma caused the scale of the logarithm value of the gear ratio. The upper scale corresponds to the output shaft on the forward stroke (16-1), the lower scale on the right side of the reverse gear (8R-1R), in the left part on the intermediate shaft. The point 0 on the middle horizontal line on the left corresponds to the primary shaft, the other point - the secondary shaft. Vertical beam corresponds to the transmission number equal to one. The inclination of the beam to the right indicates a decelerating mode: the greater the slope of the beam, the higher the value of the gear ratio. The inclination of the beam to the left (see figure 2. on the bottom left, rays 2 and 3) characterizes the work gear pair in accelerating mode. In logarithmic scale, the slope of the beam is constant on any part of the radiation diagram. Rays of pairs of external gears gearing labeled 1, 2, 3 and 4, and the rays characterizing the modes of operation of the planetary mechanism, - U=1,0; Ubah=K+1 and Uhab- K.

In support of the unit's casing 1 are coaxially arranged input shaft 2, the output shaft 3, the shaft drove 4 and output shaft 5. In parallel, they installed the intermediate shaft (axis) 6, on which are located two blocks gears external gearing 7, 8 and 9, 10. These gears are vzaimozachety respectively with gears external gearing 11, 12, 13 and 14, freely mounted on the primary 2 and secondary 3 shafts. On the secondary shaft 3 fixed sun gear 15, which is geared with satellites 16, the mouth is fixed on the axes of the carrier 17 and is geared with epicycle wheel Cam shaft 19 case epicycle wheel 18 is connected with a ring gear 20. On the shaft drove a 4 next to the ring gear 20 fixed-position crown gear 21. On the output shaft 5 near the toothed crowns 20 and 21 fixed three-position crown gear 22. In the case epicycle wheel 18 is ring gear 23. On the drive rod 17 next to the ring gear 23 is crown gear 24. Three-position crown gear 25 fixed on the inner wall of the housing unit 1 opposite the gear rims 23 and 24. Clutch switch 26 (a) and 27 (C) are installed respectively between the gears 11-12 and 13-14. Clutch switch consists of two oppositely deployed one-way clutch 28 and 29. One-way clutch 28 are mounted on the pinion gear 12, the opposite deployed one-way clutch 29 is installed on the gear 9 and interconnected plug switch 30 with the coupling 28. Three-position clutch 31 (D) with three internal toothed crowns is located on the ring gear 22 of the output shaft 5. The slider 32 is movably connected to the clutch switch 31, the slide is fixed crown gear 33 with internal and external links, external gearing mounted on the ring gear 25 of the housing 1.

Instead of the intermediate shaft 6 at a small axial distance to the shafts 2 and 3 it is possible to install axis located here by two sets of gears: 7-8 and 9-10. It is possible to install the clutch 28 on the gear 13, and the coupling 29 on the gear 8.

A slave is that KP is as follows.

Neutral condition (KP not working) is provided with installation of couplings And (26) in the middle, neutral position, in which torque from the primary shaft 2 is not transmitted to the adjacent gear 11 or 12.

The first transmission

Clutch switch (26) is in the left position (L) - (see table 2 top right), clutch switch (28 and 29) and (27) is in the right position (P), clutch switch D (31) is in the middle position (II - Ubah=To+1). In this case, the clutch And connects the gear 11 with the primary shaft 2, the clutch: (28) - connects the gears 12 and 13 (29) - disconnecting the gears 8 and 9 blocks of the intermediate gear shaft (axis) 6, coupling (27) connects the gear 14 with the secondary shaft 3, the slide ring gear 32 33 connects the ring gear 25 of the housing 1 with a ring gear 23 and stops the epicycle wheel 18 (b) relative to the body unit 1, and the coupling D (31) connects the ring gear shaft 21 led 4 gear the crown 22 of the output shaft 5. The planetary mechanism (PM) is the mode with the ratio Ubah=K+1. The upper symbol indicates that stopped link - b, lower characters on the links login (sun gear) and output (h - drove) of torque, an internal parameter PM is equal to the ratio of numbers of teeth of the epicycle wheel and sun gear - for the radiation diagram is " the execution of the PM he is 3.6; and the gear ratio GR is equal to 4.6.

Torque from the primary shaft 2 clutch switch And is transmitted to the gear 11, the gear 7 (a pair of gears 1), then the tubular shaft of the unit for a couple of gears 8-12 (2 pair), the coupling 28 to the pair of gears 13-9 (3 pair), the tubular shaft of the unit for a couple of gears 10-14 (a pair of gears 4). From gear 14 clutch switch (27) the torque is transmitted to the output shaft 3 and the sun gear 15. The sun gear 15 rotates the satellites 16, which objetivas stopped by the epicycle wheel 18, to transmit the increased torque on the carrier 17, the shaft carrier 4, the ring gear 21, the clutch switch D (31), the ring gear 22 and the output shaft 5.

Radiation diagram of this transfer of five serially connected beams: from t to medium scale left (see figure 2) beam 1 to the right, down, then beam 2 right up, beam 3 to the right down the beam 4 to the right up and then the gentle beam Ubahto 1 on the right side of the scale.

A second pass

Move the clutch to the left - coupling 29 connects the gears 8 and 9, the clutch 28 separates the gears 12 and 13, while off from work a couple of gears 2 and 3.

Torque from the primary shaft 2 is transmitted by the clutch And the gear 11, next to the gear 7 (1 pair), a tubular shaft on the gear 8, the clutch 29 to the gear 9, then trubka the WMD shaft on gear 10-14 (4 pair), then as in the previous transmission.

Radiation diagram of this transfer correspond to the three beam: 1 - right, down, 4 right up and Ubah- also right up to volume 2.

Third gear

Switchable couplings a and b from the left position to the right - coupler 26 (A) connects the input shaft 2 with the gear 12 and the clutch (28) connects the gears 12 and 13 of the secondary shaft 3, while off from work a couple of gears 1 and 2.

From the primary shaft torque coupling And is transmitted to the gear 12, on the coupling 28, the pair of gears 13-9 (3 pair), on a tubular shaft and a pair of gears 10-14 (4 pair), the coupling With the output shaft 3, then, as in the previous transmission.

Radiation diagram of this transfer correspond to rays 3, 4 and Ubahdirected from t to v.3.

The fourth transfer

Move the clutch to the left - replaced a couple of gears 3 to 2.

Torque from the primary shaft 2 is transmitted by the clutch And gears 12-8 (2 pair) in the accelerating mode, then the clutch 29 to the gear 9, the tubular shaft to the pair of gears 10-14 (4 pair) and the coupling (27) on the secondary shaft 3, then, as in the previous transmission.

Radiation diagram of this transfer corresponds to the three beam: 2, 4, and Ubahsent from t to v.4.

The fifth transmission

Switchable couplings a and C from the right, the left, and the clutch In from the left to the right. Couplings a and b are returned to the state of the first transmission. Coupling (27) disengages from the gear 14 and is connected to the gear 13 is off from work a couple of gears 4 and includes a pair of gears 3.

Torque from the primary shaft coupling And is transmitted to the pair of gears 11-7 (1 pair), a tubular shaft on a couple of gears 8-12 (2 pair) and the coupling 28 to the gear 13, the coupling With the output shaft 3 and further, as in the previous transmission.

Three beam: 1, 2 and Ubahfrom t to V.5 represent this transfer.

The sixth transmission

Switchable coupling In left - replaced a couple of gears 2 for a couple of gears 3.

To gear 7 torque is transmitted, as in the previous transmission, the clutch 29 on the pair of gears 9-13 (3 pair) in the accelerating mode, and further, as on a previous pass.

Rays 1, 3, and Ubahfrom t to V.6 conform to this transfer.

The seventh transmission

Switchable couplings a and b in the right position - a pair of gears helical geared off from work.

Torque coupling And is transmitted from the primary shaft 3 to the pinion gear 12, the coupling 28 to the gear 13 and forth, as in the previous transmission.

Ray Ubahfrom t to v.7 corresponds to the transfer.

The eighth transmission

Switchable coupling In the left position is included in the work of a pair of gears 2 and 3 in accelerating mode.

Torque the PTO is t from the primary shaft 2 is transmitted by the clutch And gears 12-8 (2 pair), coupling 29 on gear 9-13 (3 pair), the clutch and the output shaft 3. next, as in the previous transmission.

Radiation diagram this transmission is represented by rays 2, 3 and Ubahfrom t to 8.

The ninth transmission

Clutches a, b and C are returned to the position of the first transmission, and the clutch 31 and the ring gear 33 slide 32 is moved in the right position III - U=1,0 (see figure 1, bottom right). Gear 33 extends from a connection with the toothed rims 23 and 24 epicycle wheel 18 and the carrier 17. The clutch 31 left crown connects the ring gear 20 epicycle wheel 18 through Central crown with a ring gear carrier 21. For a fixed connection relative to each other of the two links in PM he blocked all three segments rotate with the same frequency. This condition PM on radiation diagram shows the vertical rays - U=1,0.

Torque to PM is transmitted as the first transmission, then directly via PM and then the toothed crowns 20 and 21, the clutch switch 31 on the ring gear 22 and the output shaft 5.

Radiation diagram this transmission is represented by five rays: the first four beam 1, 2, 3 and 4 correspond to the first gear and the fifth beam U=1,0 is directed vertically up to v.9.

The tenth transmission

Switchable coupling In the left position of the coupling are in second gear.

Torque to PM is transmitted as vtoro the transfer, and then, as the previous one.

Radiation diagram of this transfer correspond to rays 1, 4, and U=1,0.

The eleventh transmission

Roaming couplings a and b to the right into the position of the third transmission.

To PM the torque is transmitted, as in third gear, then, as in the last two gears.

Radiation diagram of the beam 3 with a slope right down the beam 4 to the right up and beam U=1,0 vertically characterize this transfer.

The twelfth transmission

Switchable coupling In the left position, all three couplings correspond to fourth gear.

To PM the torque is transmitted, as in fourth gear, then, as in the previous transmission.

Radiation diagram beams 2, 4 and U=1,0 represent this transfer.

The thirteenth transmission

Roaming clutches a and C to the left, and the coupling to the right - in the fifth gear position.

To PM the torque is transmitted, as in the fifth gear and, further, as in the previous transmission.

Rays 1, 2 and U=1,0 characterize this transfer.

The fourteenth transmission

Switchable coupling To the left.

To PM the torque is transmitted, as in the sixth transfer, further, as in the previous transmission.

Rays 1, 3 and U=1,0 conform to this transfer.

The fifteenth transmission - direct

Switchable couplings a and b to the right.

Torque to PM is sent, as in the seventh transmission, hereinafter referred to as the previous is their gear.

Ray U=1,0 is this transfer.

Sixteenth transfer - accelerating

Move the clutch to the left.

To PM the torque is transmitted, as in the eighth transmission, then, as on the last transmission.

Radiation diagram this transmission is represented by rays 2 and 3, and a vertical beam U=1,0 from so to t.16..

Reverse gears are provided with the PM when switching clutch 31, the RAM 32 and gear 33 in position I - Uhab=-K (see figure 1 top right) - with this ring gear 33 of the slide 32 connects the ring gear 24 led 17 with a ring gear 25 of the housing 1 and stops drove, the clutch 31 average ring gear connects the ring gear 20 epicycle wheel 18, and the right ring gear with a ring gear 22 of the output shaft 5. PM works in mode Uhab=-To, a sun gear 15 satellites 16, mounted on the axis is stopped drove 17, slowly rotates the epicycle wheel 18 in the opposite direction.

The first back - 1R

Set clutches a, b and C in the position of the first gear and the clutch 31 is in the position I.

To PM the torque is transmitted, as in the first and ninth speeds forward, further from the sun gear 15 of the 16 satellites on the epicycle wheel 18, and then through the tubular shaft 19, a toothed crown 20, the clutch 31, the gear Venza on the output shaft 5.

Radiation diagram, the reverse gear is represented by five rays: 1, 2, 3, 4, and Uhab=-From t to vol. 1 R.

The second back - 2R

Switchable coupling In the left position.

Torque to PM is passed as the second and tenth speeds forward, then, as on a previous pass.

Radiation diagram of this transfer correspond to the three beam: 1, 4, and Uhab=-K.

The third back - 3R

Switchable couplings a and b in the right position. Until PM torque is supplied as the third and eleventh speeds forward, then, as in the last two gears.

Radiation chart, the three beams 3, 4 and Uhab=-To characterize this transfer.

Fourth reverse - 4R

Move the clutch to the left position.

To PM the torque is transmitted, as in the fourth and twelfth speeds forward, then, as on the last transmission.

Rays 2, 4 and gentle beam Uhab=-From t to .4R represent this transfer.

The fifth back - 5R

Change the position of all three clutches.

Torque to PM is passed as the fifth and thirteenth speeds forward and next, as in the previous transmission.

Rays 1, 2 and Uhab=-Correspond to this transfer.

Sixth back - 6R

Switchable coupling In the left position

Torque to PM is passed as the sixth and fourteenth speeds forward, then, as in the previous transmission.

Rays 1, 3, and Uhab=-Correspond to this transfer.

Seventh back - 7R

Switchable couplings a and b to the right.

To PM the torque is transmitted, as in the seventh and fifteenth speeds forward, then, as on the last transmission.

Ray Uhab=-Corresponds to the transfer.

Eighth back - 8R

Move the clutch to the left position.

The torque is transmitted to the PM, as the eighth and sixteenth speeds forward, then, as in the previous transmission.

Radiation diagram beams 2, 3 and Uhab=-Correspond to this transfer.

When you change the settings of the external gears of the gearing and PM distribution transmission and skew rays will also change.

A positive effect is to expand the operational capabilities of the vehicle by increasing the number of speeds forward from fourteen to sixteen and reverse gears from one to eight with a comfortable four-way switching gears and increase efficiency with the exception of the summing operation mode PM.

Such as : valvoplasty transmission, comprising a housing in which a parallel is the al freely installed four pairs of meshed gears, external gears, gear on the intermediate shaft combined into two blocks, between the pairs of gears are clutch gear, average clutch double, consisting of two oppositely deployed one-way clutch switch installed on the gears and related plug switch, the output shaft is fixed sun gear of the simple three-tier planetary mechanism, barrel epicycle wheel, shaft carrier and output shaft are adjacent sprockets on the ring gear output shaft mounted three-position clutch switch, wherein a sun gear mounted on the secondary shaft, coaxially to the primary shaft, the housing epicycle wheel tubular shaft connected to the gear ring gear the crown shaft drove off, the clutch switch on the gear output shaft has three internal gear on the slide clutch switch is rigidly fixed ring gear with internal and external links, external toothing of which is connected with the three-position ring gear housing Assembly opposite the toothed crowns were taken and body epicycle wheel.



 

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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.

SUBSTANCE: input shaft 2 and primary shaft 3 are coaxially installed in supports of gearbox housing. Secondary shaft 4, carrier shaft 5 and output shaft 6 are arranged parallel to coaxial shafts 2 and 3. Gear 7 is fixed on primary shaft 3, gear 8 is freely fitted at one side and gear cluster consisting of two gears 9 and 10 is installed at other side. Gear cluster consisting of gears 11 and 12 engaging with gears 8 and 7 of primary shaft and gears 13 and 14 engaging with cluster of gears 9 and 10 on primary shaft are installed on secondary shaft 4. Sun gear 15a of planetary mechanism is secured at output of secondary shaft 4, said gear being engaged with planet pinions 16 arranged on axles of carrier 17H. Planet pinions 16 are in meshing with epicyclic wheel 18b. Gear 8 is connected by tubular shaft 19 with gear rim 20, gear rim 21 is secured on primary shaft 3, and three-position gear rim 22 is secured on input shaft 2, three-position shifter clutch 23A being fitted on gear rim 22. Two position twin clutch B consists of clutches 24 and 25 interconnected by shifter fork 26. Clutch 24 is installed on gear rim of gear 7 of primary shaft 3, and clutch 25, on gear rim of gear 13 of secondary shaft 4. Two-position clutch 27C is fitted on hub of secondary shaft 4 between gears 13 and 14. Gear rim 28 is secured on tubular shaft 29 of housing of epicyclic wheel 18. Two-position gear rim 30 is secured on carrier shaft 5. Three-position gear rim 31 is secured on output shaft 6 which carries shifter clutch 32 connected for sliding with slider 33. Gear rim 34 with internal and external meshing is secured on slider 33, external teeth being engaged with three-position gear rim 35 of housing 1, and gear rim 36 of carrier 17 and gear rim 37 of housing of epicyclic wheel 18 are arranged opposite to external gearing.

EFFECT: reduced metal usage, simplified design of gearbox.

2 dwg

FIELD: transport engineering.

SUBSTANCE: proposed gearbox contains coaxial input, primary and secondary shafts and countershaft parallel to them, two-position twin clutch consisting of two one-way clutch members intercoupled by shifter fork, shifter clutch installed on gear rim of input shaft and shifter clutch installed on gear rim of outer shaft. Simple three-link planetary mechanism is installed on secondary shaft of gearbox.

EFFECT: enlarged operating capabilities of vehicle owing to increased number of speeds and range of gearbox.

2 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in vehicles and in drives of mounted equipment of special vehicles. Shifter clutch of gearbox output shaft is brought out of reduction gear part. Cluster of two gears is freely fitted on secondary shaft and one gear is fixed. Shifter clutch is arranged in between, being coupled by slider with other clutch arranged between gears of primary shaft. Carrier shaft gear rim is two-position, and gear rim of output shaft is three-position one. Shifter clutch on said rim is provided with three internal gear rims. Gear rim with internal and external meshings is rigidly secured on slider of shifter clutch. External gearing of rim is engaged with three-position gear rim of housing.

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; 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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