Multiple-speed misaligned semiplanetary gearbox

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: according to invention, gear 14 is secured on primary shaft 3, and gear 13 is secured on first tubular shaft 9 freely fitted on primary shaft 3. Gear rims 21 and 22 are fitted on shafts 3 and 9. Input shaft 2 with hub of three-position shifter sleeve 23 and additional driving shaft 4 are installed coaxially to shaft 3. Two gears 17 and 18 in meshing with gears 19 and 20 of secondary shaft 5 are secured on shaft 4. Gear 19 is fitted on shaft 5. Gear 20 is secured on second tubular shaft 10 freely installed on shaft 5. Gear rims 24 and 25 are secured on shafts 5 and 10. Shaft 6 with hub of two-position shifter sleeve 26 and sun gear 27 of planetary mechanism is installed coaxially to shaft 5. Gear 27 engages through planet pinions 31 with epicyclic wheel 32. Planet pinions 31 are freely fitted on axles of carrier 33. Two gear rims 34 and 35 are arranged on periphery of housing of carrier 33. Shaft 7 of carrier 33 with two position gear rim is arranged coaxially to shaft 5 and shaft 6. Third tubular shaft 11 of housing of epicyclic wheel with gear rim 38 is freely fitted on shaft 7. Output shaft 8 with hub of three-position shifter sleeve 40 is arranged coaxially to shaft 7. Sleeve 40 is movably coupled by guide 41 with two-rim shifter sleeve 42 arranged between gear rim 37 of housing 36 of epicyclic wheel 32 and gear rim 43 of gearbox case provided with two inner gear rims and one outer gear rim.

EFFECT: perfected design owing to reduction of metal usage and complexity.

2 dwg

 

The invention relates to transport machinery, transmission vehicles.

Closest to the proposed non-axial multi-stage gearbox (MCP) is a non-axial MCP 16 R 8 (16 speeds forward and 8 reverse gears) patent RU NO. 2050290, 60 TO 17/08 (20.12.95. Bull. N 35).

The CP consists of a body placed in parallel the primary and secondary shafts, arranged them in four rows of pairs of meshed gears, three-position clutch switch located between the first gear shaft and the last gear of the output shaft, between the average ranks of a dual gear-position clutch, consisting of two oppositely-deployed couplings unilateral action, interconnected with a fork switch, one coupler is installed on the ring gear of the primary gear shaft and the other clutch is installed opposite to the first clutch to the ring gear of the secondary gear shaft, coaxially with the secondary shaft are simple three planetary gear with the clutch switch and the output shaft, the secondary shaft freely mounted a block of two gears that are meshed with the gear shaft.

Described MCP compared with conventional MCP traditional layout (four basic gearbox with front splitter and rear plan is ary dual high) has good structural characteristics, but for switching States of the planetary mechanism uses two independent clutch switch, with three couplings switching shaft of the gearbox received patitofeo MCP, which complicates the management of the transmission unit; two three-position clutch switch located inside shaft of the gearbox, which increases the size and intensity of the MCP.

Object of the invention is the improvement of the design of the MCP.

The technical result is achieved due to the further reduction of metal consumption and design complexity of the MCP.

The achievement of the technical result is ensured by the fact that non-axial multi-stage preplanetary transmission, comprising a housing placed in parallel the primary and secondary shafts, arranged them in four rows of pairs of meshed gears, between the average ranks of a dual gear-position clutch, consisting of two oppositely-deployed couplings unilateral action, interconnected with a fork switch, one coupler is installed on the ring gear of the primary gear shaft and the other clutch is installed opposite to the first clutch to the ring gear of the secondary gear shaft, coaxially with the secondary shaft are simple three planetary gear with the clutch switch and the output shaft, wtorek the Ohm shaft freely mounted a block of two gears, which is meshed with the gear shaft, characterized in that one gear is fixed on the primary shaft and a second gear fixed to the first tubular shaft freely mounted on the primary shaft, the first tubular and the primary shafts fixed sprockets coaxially primary shaft is the input shaft to the hub of the three-position clutch switch and an additional drive shaft, on which are fixed two gear meshed with gear secondary shaft, one gear mounted on the secondary shaft, a second gear fixed to the second tubular shaft freely mounted on the secondary shaft, secondary and second tubular shafts fixed gear crowns, coaxially with the output shaft has a shaft with a hub-position clutch switch and a sun gear of the planetary mechanism, a sun gear via satellites geared with epicycle wheel, satellites freely mounted on axes drove, on the periphery of the casing drove there are two gear shaft drove with two-position ring gear is located coaxially with the output shaft and the shaft of the sun gear on the shaft drove freely set the third tubular shaft housing epicycle wheel with a ring gear, a coaxial shaft carrier is the output shaft with the hub of the three-position clutch switch, is that the clutch is a lever movably connected with dvuhvekovoi clutch switch, located between the toothed crowns corps epicycle wheel and the transmission housing, having two internal ring gear and one outdoor gear.

Two clutches are connected by a leash, simplify switching the three States of the planetary mechanism; two couplings made outside the shaft part of the body, reduce the size and intensity of the transmission Assembly.

Figure 1 shows the kinematic diagram of the 16-speed non-axial preplanetary (Volynoblenergo) transmission.

Figure 2 presents the radial chart MCP with tables of the provisions of the coupling switch to a different transmission.

On the horizontal scale of the chart in logarithmic form shows the values of ratios of pairs of gears and gear. Above the upper scale marked forward gears: 16-1, under the lower scale - reverse gear: 8R-1R. The upper and lower horizontal lines correspond to the ratios on the output shaft, the average horizontal - on the secondary shaft. The point 0 to the left on the lower horizontal line corresponds to the input shaft. The inclination of the beam to the right indicates a decelerating mode of operation of the pair of gears, the larger the slope, the greater the gear ratio.

The inclination of the beam to the left characterizes accelerating mode of the pair of gears. On any part of the radiation diagram the slope of the beam constant for the each of the pair of gears.

In the tables, the letter L indicates left position of the clutches a, b and C, and the letter P on the right position of these couplings. Clutch D provides three States of the planetary mechanism (PM): I-Uhab=- ; II-Ubah=To+1; III-U(bh)=1,0 where K is an internal parameter PM is equal to the ratio of the number of teeth of the epicycle wheel (b) to the number of teeth of the sun gear (a), the upper index indicates the stopped element, indexes down - links input and output torque; indices (bh) indicate the locked state of the PM - two of the link: epicycle wheel (b), and led (h) are closed.

In support of a corps MCP 1 (see figure 1) coaxially mounted input shaft 2, the input shaft 3 and an additional drive shaft 4. Parallel coaxial shafts 2, 3 and 4 placed secondary shaft 5, the shaft of the sun gear 6, the shaft carrier 7 and the output shaft 8. On the primary shaft 3 is freely mounted to the first tubular shaft 9, the second tubular shaft 10 is freely mounted on the secondary shaft, the third tubular shaft 11 is also freely mounted on the shaft drove 7. The tubular shaft 12 of the gear train freely mounted on the secondary shaft 5 at the level of the gear shaft 3. Gear 13 fixed to the first tubular shaft 9 and the gear 14 fixed on the primary shaft 3. The gears 13 and 14 are meshed with gears 15 and 16, mounted on the tubular shaft 12. Gears 17 and 18 mounted on the more the positive control shaft 4 and meshed with the gear 19 of the output shaft 5 and 20 of the second tubular shaft 10. Crown gear 21 fixed to the first tubular shaft 9, next to him on the primary shaft 3 fixed crown gear 22. On the hub of the input shaft 2 is a three-position clutch switch 23 (a). Crown gear 24 mounted on the second tubular shaft 10, next to it on the secondary shaft 5 is fixed ring gear 25. Dip the clutch 26 (C) is located on the shaft 6 sun gear 27. Dip dual clutch comprises two clutch: clutch 28 are mounted on the toothed crown gear 14 of the primary shaft 3, and the opposite deployed clutch 29 is on the toothed crown gear 19 of the secondary shaft 5, the clutch interconnected with a fork switch 30. Satellites 31 meshed with the sun gear 27 and the epicycle wheel 32. The case took 33 mounted on the shaft carrier 7, on the periphery of the body led 33 are sprockets 34 and 35. On the third tubular shaft fixed to the housing 36 epicycle wheel 32, on the outer surface of the fixed housing two-position crown gear 37. Ring gear 38 is fixed on the third tubular shaft 11 near the dip ring gear 39 fixed on the shaft drove 7. On the hub of the output shaft 8 mounted three-position clutch switch 40, which is leash 41 movably connected with dvuhvekovoi clutch 42, located between the dip toothed rims 43 of the housing box is heredoc and 37 of the body 36 epicycle wheel 32.

Pets another location couplings: coupling 28 on the ring gear of the gear 17, and the clutch 29 is on the toothed crown gear 16.

Work multistage non-axial preplanetary transmission is as follows:

16-I transfer

Couplings a and b are in the left position, the clutch is on the right, the clutch D is in the third position (see figure 2, top left).

Torque (see figure 1) from the input shaft 2 by a coupling 23 (a) is transmitted to a ring gear 22, the primary shaft 3, a pair of gears 14-16, further coupling 29 to the output shaft 5 (coupler 28 in this position separates the gears 14 and 17), a ring gear 25 and the sleeve 26 on the shaft 6 sun gear 27. The coupling 42 connects the ring gear 35 of the casing drove 33 with the ring gear 37 of the housing 36 epicycle wheel 32, the planetary mechanism is locked and all three of his team rotate at the same speed. The coupling 40 connects the ring gear 39 of the shaft carrier 7 with the output shaft 8. The output shaft 8 rotates at a speed greater than the speed of the input shaft 2.

Radiation diagram this transmission is represented by two beams: the beam from t on the lower horizontal left (see figure 2) up to the left to the middle horizontally and then vertically up to t.16..

15-I transfer

Switchable clutch in the right position. Instead of a pair of gears 14-16, the work included a pair of gears 17-19.

To gear 14 torque peredatsja on a previous pass, next on the coupling 28 to the pair of gears 17-18, then as in the previous transmission.

Radiation diagram this transfer is depicted by rays: III from t right up and then the beam vertically to a t.15.

14-I transfer

Return the clutch to the left position, the coupling With switchable also left three couplings in the left position.

Torque from the input shaft to the clutch 29 is transmitted as the 16-th transmission, then a pair of gears 19-17, additional drive shaft 4, a pair of gears 18 to 20, the third tubular shaft 10, a toothed crown 24 and the sleeve 26 (C) on the shaft 6 sun gear 27, and then as in the previous transmission.

Radiation diagram of this transfer owns four beam: beam II from t upward to the left, then the beam III down the left, then the beam IV right up and vertical beam to t.

13-I transfer

Switchable clutch in the right position. Instead of pairs of gears 14-16, 19-17 and 18-20 in the work of only a pair of gears 18-20.

To the gear 17 and the torque is transmitted on 15-th transmission, then an additional drive shaft 4, a pair of gears 18-20, then as in the previous transmission.

Radiation diagram of the beam IV from t right up and vertical beam to v.13 characterize this transfer.

Transfer from the 12th through 9 differs from the previous transmission only switching clutch And from the left position to the right.

12-I transfer

Swap the tea clutches a and C in the right position, and the clutch is to the left. Instead of a pair of gears 18-20, the work included a pair of gears 13-15.

Torque from the input shaft 2 clutch (A) 23 is transmitted to the ring gear 21, the first tubular shaft 9 by a pair of gears 13 and 15, the tubular shaft 12, the clutch 29 to the output shaft 5, hereinafter referred to as the 15-th transmission.

Radiation diagram of the beam I from t right up and vertical beam to vol.12 characterize this transfer.

11-I transfer

Switchable clutch in the right position - all couplings in the right position. To a pair of gears 13 and 15 in the operation further includes a pair of gears 16-14 and 17-19.

To the tubular shaft 12 of the torque is transmitted as in the previous transmission, then a pair of gears 16-14, the clutch 28, and then on the 15th the transfer.

Radiation diagram of this transfer owns four beam: beam I from t right up, then the beam II right down next beam III right up and vertical beam to t.

10-I transfer

Switchable clutch In and to the left position is off from work a couple of gears 16-14 and include a couple of gears 18-20.

To the tubular shaft 12 of the torque is transmitted as in the previous transmission, then the clutch 29, the pair of gears 19-17, additional drive shaft 4, then on the 13-th transmission.

Radiation diagram of this transfer owns four beam: beam I from t right up, then the beam III down the left, then the beam IV right up the vertical beam to V.10.

9-I transfer

Switchable clutch in the right position - turn off from work a couple of gears 19-17 and include a couple of gears 16-14.

To the tubular shaft 12 of the torque is transmitted as in the previous transmission, then a pair of gears 16-14, the clutch 28, the additional drive shaft 4, then on the 13-th and 10-th transmission.

Radiation diagram of this transfer owns four beam: beam I from t right up, then the beam II to the right, down, then the beam IV right up and vertical beam to v.9.

Transmission 8-th and 1-th differ from the gear 16 on the 9th only switching clutch D from position III to position II. In this state, the planetary mechanism is unlocked. Clutch 42 right inner crown meshed with a ring gear 37 of the housing 36 epicycle wheel 32 (see figure 1 at the top of the planetary mechanism), it is right outside crown meshed with a ring gear 43 of the transmission housing and stops epicycle wheel 32 relative to the housing 1. Torque acts on the sun gear 27 and is removed from the shaft drove 7 - planetary mechanism operates in the mode of the gearbox with a transmission ratio equal To+1. For example:

8-I transfer

Couplings a and b are in the left position, the clutch is on the right, the clutch D is in the II position (see figure 2 at the top in the middle part).

Torque (see figure 1) from the input shaft 2 by a coupling 23 (a) is transmitted zu the striated crown 22, the primary shaft 3, a pair of gears 14-16, further coupling 29 to the output shaft 5 (coupler 28 in this position separates the gears 14 and 17), a ring gear 25 and the sleeve 26 on the shaft 6 sun gear 27. The sun gear rotates the satellites 31, which objetivas relatively stopped epicycle wheel 32, rotate the housing 33 and the shaft drove 7 slow speed. The coupling 40 connects the ring gear 39 of the shaft carrier 7 with the output shaft 8. The output shaft 8 rotates at a speed less than the speed of the input shaft 2, but with increased torque.

Radiation diagram this transmission is represented by two rays: ray II from t on the lower horizontal left (see figure 2) left up to the average horizontal and forth gently right up to 8.

1st gear

Switchable couplings a and b in the right position, and the clutch With the left.

To the sun gear 27 and the torque is transmitted on 9-th transmission, hereinafter referred to as the 8-th transmission.

Radiation diagram of this transfer owns four beam: beam I from t right up, then the beam II to the right, down, then the beam IV right up and gently sloping beam right up to vol.1

Reverse gear is different from the previous transmission only switching clutch D from position II to position I.

Clutch 42 left inner crown meshed with a ring gear 34 of the housing 33 led (see figure 1 below planetary me what Anisman), it is the same left, but the outer crown meshed with a ring gear 43 of the transmission housing and stops drove 33 relative to the housing 1. Torque acts on the sun gear 27 and is removed from epicycle wheel 32, the planetary mechanism operates in the mode of the gearbox with a transmission ratio equal To, the output shaft 8 rotates in the direction opposite to the rotation of the sun gear 27. For example:

1st reverse gear

Couplings a and b are in the right position, the coupling - in the left, the clutch D is in the I position (see figure 2 bottom right).

Torque (see figure 1) from the input shaft 2 to the sun gear 27 is passed as the 1st forward gear. The sun gear 27 rotates satellites 31, which objetivas relative to the stopped carrier 33, rotate epicycle wheel 32, his body 36 and the third tubular shaft 11 with slow speed in the direction opposite to the rotation of the sun gear 27. The coupling 40 connects the ring gear 38 of the third tubular shaft 11 to the output shaft 8.

Radiation diagram of this transfer owns four beam: beam I from t right up, then the beam II to the right, down, then the beam IV right up and gently sloping beam left down to .1R.

8-I reverse gear

Couplings a and b are in the left position, the clutch is on the right, the clutch D is in the first position.

Torque moment is (see 1) from the input shaft 2 by a coupling 23 (a) is transmitted to a ring gear 22, the primary shaft 3, a pair of gears 14-16, further coupling 29 to the output shaft 5 (coupler 28 in this position separates the gears 14 and 17), a ring gear 25 and the sleeve 26 on the shaft 6 sun gear 27, hereinafter referred to as a previous pass.

Radiation diagram this transmission is represented by two beams: the beam from t on the lower horizontal left (see figure 2) left up to the average horizontal and forth gently sloping right down to .8R.

Multi-stage non-axial preplanetary transmission, comprising a housing placed in parallel the primary and secondary shafts, arranged them in four rows of pairs of meshed gears, between the average ranks of a dual gear-position clutch, consisting of two oppositely-deployed couplings unilateral action, interconnected with a fork switch, one coupler is installed on the ring gear of the primary gear shaft and the other clutch is installed opposite to the first clutch to the ring gear of the secondary gear shaft, coaxially with the secondary shaft are simple three planetary gear with the clutch switch and the output shaft, the secondary shaft freely mounted a block of two gears that are meshed with the gear shaft, characterized in that one gear Zack is Alena on the primary shaft, and the second gear fixed to the first tubular shaft freely mounted on the primary shaft, the first tubular and the primary shafts fixed sprockets coaxially primary shaft is the input shaft to the hub of the three-position clutch switch and an additional drive shaft, on which are fixed two gear meshed with gear secondary shaft, one gear mounted on the secondary shaft, a second gear fixed to the second tubular shaft freely mounted on the secondary shaft, secondary and second tubular shafts fixed sprockets coaxially with the output shaft has a shaft with a hub-position clutch switch and a sun gear of the planetary mechanism, the sun gear through satellites geared with epicycle wheel, satellites freely mounted on axes drove, on the periphery of the casing drove there are two gear shaft drove with two-position ring gear is located coaxially with the output shaft and the shaft of the sun gear on the shaft drove freely set the third tubular shaft housing epicycle wheel with a ring gear, a coaxial shaft carrier is the output shaft with the hub of the three-position clutch switch, this clutch is a lever movably connected with dvuhvekovoi clutch switch located between the toothed crowns is orpus epicycle wheel and the transmission housing, having two internal ring gear and one outdoor gear.



 

Same patents:

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: in proposed coaxial shaft-and-planetary transmission gear 10 on primary shaft 2 is secured and is in meshing with gear 7 provided with rim of increased width and freely fitted on intermediate shaft 6. Gear 11 of secondary shaft 3 has also rim of increased width near gear rim of gear 10 of primary shaft 2. shifter sleeve member 24 fitted on said gear rims is coupled with other sleeve member 25 by shifter fork 26, sleeve member 25 being installed on gear rims of gears 7 and 8 of intermediate shaft 6. Gear rim 19 of output shaft of carrier 15 is two-position one. Gear rim 20 of output shaft of set 5 is three-position one, and shifter sleeve 28 on said rim is provided with three internal gear rims. Gear rim 31 with internal and external meshing is teeth rigidly secured on slider 30 of shifter sleeve 28, external meshing teeth being coupled with three-position gear rim 23 of housing of set 1.

EFFECT: increased range of gear ratios of shaft reduction gear at reduced overall dimensions and metal usage, improved gear shift mechanism of planetary mechanism.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: mechanical amplifier comprises power differential (1), comparing differential (30), adjusting differential (2), control differential (36), and two self-braking mechanisms (3) and (4). The input of the power differential (1) is connected with the drive and input of control differential (2). Central wheels (17) and (18) of the power differential are secured to driven links (15) and (16) of the self-braking mechanisms and connected with central wheels (32) and (33) of the comparing differential so that the central wheels of the comparing differential rotate in opposite directions. Driving links (13) and (14) of the self-braking mechanisms are connected with central wheels (19) and (20) of the adjusting differential and central wheels (42) and (43) of the control differential so that the central wheels of the control differential rotate in opposite directions.

EFFECT: enhanced reliability and expanded functional capabilities.

1 dwg

Drive (versions) // 2278309

FIELD: mechanical engineering; devices for control of rotational speed of working member shaft.

SUBSTANCE: proposed drive has unadjustable electric motor, adjustable electric motors, input shaft 1 and output shaft 2, gear trains, differential gear trains formed by two wave gear trains with common wave generator 3 and worm transmissions and differential gear. Worm shafts 11 and 12 are set in rotation from adjustable electric motors. External gear wheels 6 and 7 of wave gear trains are coupled with worms 11 and 12. Internal gear wheels 9 and 10 of wave gear trains are kinematically linked with differential gear wheels 19 and 20 which are connected with output shaft 21 of drive. Two wave gear trains are chain-type in construction and are related as follows: Zch1+Zch2=2Zext; Zch1+Z=Zch2-Z, where Zch1 and Zch2 is number of rollers in chains of first and second wave gear trains; Zext is number of teeth of external gear wheel of wave gear drives thrown into engagement with rollers of chains; 2Z is difference of rollers in chains.

EFFECT: possibility of changing the direction of rotation and rotational speed of shaft of working member in wide range; increased speed of response; enhanced reliability.

5 cl, 3 dwg

FIELD: agricultural engineering; offroad tractor.

SUBSTANCE: invention relates to driving axle with suspension and agricultural tractor with such axle which has central housing with build-in final drives and left-hand and right-hand axle housings suspended by means of upper and lower adjusting arms, with axle-shafts projecting from axle on which wheel-and-tire units are installed. Constant-velocity universal joint is installed between fitted-in final drives and axle-shafts. Said universal joint has pair of journal members and coupling holder radially enclosing driving and driven races of joint, thus minimizing axial length of universal joint providing arrangement of wheels on axle-shafts at width of 1524 mm.

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39 cl, 15 dwg

FIELD: transport engineering.

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1 dwg

FIELD: transport engineering.

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EFFECT: reduced overall dimensions adapted for mounting transfer case on vehicles.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: gear transmission comprises planetary reduction gear and worm pair which engages the planetary reduction gear. Worm (1) of the worm pair is mounted for permitting rotation and axial movement along the driving shaft of the gear transmission and is kinematically connected with satellite (7) of the planetary reduction gear. Driving shaft (2) carries small central wheel (9) of the planetary reduction gear and kinematically connected with satellite (10) of the planetary reduction gear. Satellite (10) is kinematically connected with worm wheel (3). The axle of wheel (3) freely rotates around carrier (4). The axle of large central wheel (8) of the planetary reduction gear is the driven shaft of the gear transmission.

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The invention relates to the holonomic transmission with stepless change of torque and can be used in machinery, vehicles, machine tools, and other objects and systems

Transmission // 2237207
The invention relates to vehicles, particularly to transmissions of the self-propelled agricultural machines, equipped with hydrostatic drive

Transmission // 2235238
The invention relates to transport machinery, namely, gear boxes with fixed axle shafts

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: in proposed coaxial shaft-and-planetary transmission gear 10 on primary shaft 2 is secured and is in meshing with gear 7 provided with rim of increased width and freely fitted on intermediate shaft 6. Gear 11 of secondary shaft 3 has also rim of increased width near gear rim of gear 10 of primary shaft 2. shifter sleeve member 24 fitted on said gear rims is coupled with other sleeve member 25 by shifter fork 26, sleeve member 25 being installed on gear rims of gears 7 and 8 of intermediate shaft 6. Gear rim 19 of output shaft of carrier 15 is two-position one. Gear rim 20 of output shaft of set 5 is three-position one, and shifter sleeve 28 on said rim is provided with three internal gear rims. Gear rim 31 with internal and external meshing is teeth rigidly secured on slider 30 of shifter sleeve 28, external meshing teeth being coupled with three-position gear rim 23 of housing of set 1.

EFFECT: increased range of gear ratios of shaft reduction gear at reduced overall dimensions and metal usage, improved gear shift mechanism of planetary mechanism.

2 dwg

FIELD: transport engineering; transmissions.

SUBSTANCE: invention can be used in automobiles, tractors, road building machines. Gear 11 of transmission is coupled with primary shaft 2. Additional simple three-members planetary mechanism has two gear rims, gear rim 22 of partition of housing of set 1 and shifter sleeve 23. Main planetary mechanism has gear rims 31, 32 of carrier 25 and housing of epicyclic gear 26 opposite to gear rim of set housing. Gear rims 28, 29, 30 of tubular shaft 27 of housing of epicyclic gear 26, output shaft of carrier 25 and output shaft of set are arranged close to each other. Shifter sleeve D is connected by fork 39 and slider 40 with gear rim 41 with internal and external meshing teeth arranged on gear rim 33 of set housing.

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2 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: gear 11 and cluster of gears 9 and 10 are freely fitted on transmission secondary shaft 3. Shifter sleeve 24 (B) is arranged on hub of secondary shaft 3 between gear 11 and cluster of gears 9 and 10. Two gears 7 and 8 on primary shaft 2 are united into cluster and are arranged opposite to shifter sleeve of secondary shaft 3. Gear rim 18 of output shaft 4 of carrier 14 is two-position one. Gear rim 19 of output shaft 5 of set 1 is three-position one. Shifter sleeve 25 (C) on said rim has three internal gear rims. Gear rim 28 with internal and external meshing teeth is rigidly secured on slider 27 of shifter sleeve 25(C), external meshing teeth of gear rim being engaged with three-position gear rim of set housing.

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2 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to gearbox of automobiles, crawler vehicles, two-member crawlers, crawler chassis of loggers, etc. proposed hydromechanical transmission has input shaft 1 and output shaft 2, four differential mechanisms, each including carrier, planet pinions, sun and epicyclic gears and six friction control members in form of clutches 11, 12 and brakes 7-10. Three differentials, whose sun gears 31, 27, 23 are installed on input shaft 1, form main planetary gear transmission. Epicyclic gears 28, 20 of first and third differentials are connected with carrier 25 of second differential. Carrier 29 of first differential is connected with brake 7 and, through friction clutch 11, with input shaft 1. Carrier 21 of third differential is connected with output shaft 2 through fourth differential used as divider at output.

EFFECT: simplified design, reduced speed of rotation of differential members and friction members, multipurposeness of transmission.

2 dwg

FIELD: transport engineering; automatic transmissions.

SUBSTANCE: invention relates to fixed-ratio planetary gear transmissions. Proposed transmission with seven forward speeds and one reverse speed, has case 1, torsional vibration damper 2, input link 3, output link 4 and planetary reduction gear including three planetary gear trains, two friction clutches and four friction brakes. First planetary gear train consists of sun gear 5, planet pinion carrier 6 and ring gear 7. second planetary gear train consists of sun gear 8, planet pinion carrier 9 and ring gear 10. Third planetary gear train consists of sun gear 11, planet pinion carrier 12 and ring gear 13. Input link 3 is connected by friction clutch 14 with intercoupled ring gear 10 and sun gear 11. Input link 3 is connected by friction clutch 15 with intercoupled carrier 9 and carrier 12. Sun gear 5 is coupled with input link 3. Input link 3 is coupled with torsional vibration damper 2. Carrier 6 is connected with transmission case 1 by friction brake 10. Friction brake 17 connects intercoupled ring gear 7 and sun gear 8 with transmission case 1. Friction brake 18 connects intercoupled carrier 12 and carrier 9 with transmission case 1. Friction brake 19 connects intercoupled sun gear 11 and ring gear 10 with transmission case 1. Ring gear 13 is coupled with output link 4 of transmission.

EFFECT: enlarged kinematic capabilities of transmission and increased its service life.

1 dwg

FIELD: transport engineering.

SUBSTANCE: active transmission is designed for cross-country vehicles and it includes gearbox 2, transfer case 3 with mechanism to distribute torque between axles and transfer case 4 with mechanism to distribute torque among wheels. Transfer case of vehicle has housing, input and two output shafts. Input shaft is coupled through two floating shafts with double planetary reduction unit whose carriers are coupled through differential. Two central wheels of planetary reduction unit are coupled through differential arranged in common housing with first one. One of differentials in transfer case connecting carriers can be replaced by rigid tie including damping device.

EFFECT: increased cross-country capacity of vehicle, reduced load on engine and transmission, optimization of gearshift mechanism and independent operation of output shaft reverser.

6 cl, 15 dwg

FIELD: mechanical engineering.

SUBSTANCE: hydromechanical gear box comprises crankcase (1), torsional vibration damper (2), input link (3), output link (4), planet gear made of three planet rows, two friction clutches, and four friction brakes. First planet row is made of solar pinion (5), carrier (6) of satellites, and corona pinion (7). Second planet row is made of solar pinion (8), carrier (9) of satellites, and corona pinion (10). Third planet row is made of solar pinion (11), carrier (12) of satellites, and corona pinion (13). Input link (3) is connected with corona pinion (13) and carrier (9) through friction clutch (14). Input link (3) is connected corona pinion (10) and solar pinion (11) through friction clutch (15). Carrier (6) is connected with input link (3). Input link (3) is connected with torsional vibration damper (2). Friction brake (16) connects corona pinion (10) and solar pinion (11) with crankcase (1) of the gear box. Friction brake (17) connects corona pinion (13) and carrier (9) with crankcase (1) of the gear box. Friction brake (18) connects solar pinion (5) and solar pinion (8) with crankcase (1) of the gear box. Corona pinion (7) is connected with crankcase (1) through friction brake (19). Carrier (12) is connected with output link (4) of the gear box.

EFFECT: expanded functional capabilities and prolonged service life.

1 dwg

Block gear box // 2287439

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises housing and pinions for transmitting rotation of the driving shaft to the driven shaft. The pinions are interconnected in two blocks and define a gear box of pinion blocks. The pinions of each block are axially aligned and arranged in the order of increasing or decreasing of their outer diameter. Each driving pinion engages only the driven pinion excluding the pinions of the reverse motion that are interconnected through the parasite pinion. The axles of the blocks are the axles of the shafts inside each block. The shafts are parallel. The pinion blocks reciprocate in the housing along the guides. One of the guides has locators. The spline collars of the shafts disengage the operating pinions.

EFFECT: enhanced reliability and prolonged service life.

8 dwg

Transmission // 2284925

FIELD: transport engineering.

SUBSTANCE: invention relates to design of planetary transmission which can be used in automatic transmission systems controlled by electronic and hydraulic control units for use in road vehicles. Proposed transmission contains planetary reduction gear, carrier 6 of planetary gear train being output member 4 of transmission. Carrier 9 of second planetary gear train is coupled with crown gear (epicycle) 7 of first planetary gear train. Sun gear 5 of first planetary gear train is coupled with epicycle 10 of second planetary gear train and by brake 16, with transmission case. Sun gear 8 of second planetary gear train is coupled with sun gear 11 of third planetary gear train and by brake 18, with transmission case. Input member 3 is coupled with carrier 12 of third planetary gear train. Epicycle 13 of third planetary gear train is coupled by brake 19 with transmission case. Input member 3 is coupled by clutch 14 with carrier 9 of second planetary gear train. Epicycle 7 is provided with brake 17 for coupling with transmission case. Input member 3 is coupled by clutch 15 with sun gear 5. Input member 3 is coupled also with torsional vibration damper 2. Reduction of overall dimensions of transmission makes it possible to enlarged range of vehicle in which proposed transmission with such kinematic diagram can be used, and dynamic characteristics of vehicle are considerable improved owing to change of design of transmission and change of gear ratios of planetary gear trains and order of in-pair engagement of friction control member.

EFFECT: enlarged kinematic capabilities of transmission, increased service life, reduced mass owing to dispensing with torque converter and reduced number of transmission components.

1 dwg

Vehicle // 2283243

FIELD: transport engineering; entertainments.

SUBSTANCE: proposed vehicle contains traction motor 47 and stepless gearbox - variable-speed drive. Used as variable-speed drive can be amplifier consisting of power differential 1, comparing differential 30, regulating differential 2, control differential 36 and two-self-braking mechanisms 3, 4. Input of power differential is connected with traction motor and input of regulating differential, central gears 17, 18 of power differential are connected with driven links 15, 16 of self-braking mechanism and with central gears 32, 33 of comparing differential to provided rotation of central gears of comparing differential in opposite directions. Driving links 13, 14 of self-braking mechanisms are connected with central gears 19, 20 of regulating differential and central gears 42, 43 of control differential to provide rotation of central gears of control differential in opposite directions, and change of gear ratio is carried out by means of bicycle-type pedal unit 46 mechanically coupled with control differential with possibility of changing speed of rotation of its central gears. Central of regulating differential are closed by speed equalizer 41.

EFFECT: provision of vehicle with ratio change and reversing by means of bicycle-type pedal drive.

2 cl, 1 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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