Coaxial shaft-and-planetary transmission
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.
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 cars. (Vehicles: 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 2217325 C1 (bull. No. 33 dated 27.11.2003).
The transmission includes a housing unit in which there are three coaxial gearbox with three pairs of vzaimozachetnykh gear external gear, the gear on the primary and secondary shafts installed freely between them are two clutch gear, the gear on the intermediate shaft are combined in a block, the output of the reducer is a simple three planetary gear with planet carrier, satellites, epicycle wheel and a sun gear mounted on the secondary shaft, primary, secondary shaft of the gearbox output shaft carrier and output shaft Assembly are aligned, the body is three-shaft gear, a tubular shaft carrier and the housing epicycle wheel are near the advantage is these sprockets case epicycle wheel on the other hand, the output shaft carrier and output shaft Assembly are adjacent sprockets on the ring gear of the output shaft Assembly is installed, the clutch switch, which has two internal gear it with a fork switch and a slider movably interconnected with the clutch switch, having two internal ring gear mounted on the ring gear gear case.
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 due to the increased size of the gear freely mounted on the primary shaft, which limits the value of the gear ratio engaged, difficult shifting when changing direction of movement, as between the sub-bands, reverse and low gear is a subrange of the highest gear, the complicated design of the clutch switch, stopping drove or epicycle wheel relative to the housing.
The problem to which the invention is directed, is to expand the operational capabilities of the vehicle while simplifying the design and reducing the metalloemkost transmission Assembly.
The problem is solved due to the achievement of the technical result consists in increasing the range of the gear ratio shaft of the gearbox by reducing its size and metal, the improvement of the gear of the planetary mechanism.
This technical result is achieved by coaxially valvoplasty transmission includes a housing unit in which there are three coaxial gearbox with three pairs of vzaimozachetnykh gear outer gear, the two gears on the intermediate shaft are combined in a block, gears on the secondary shaft of the gearbox is installed freely between them is a clutch gear, the output gear is a simple three planetary gear with planet carrier, satellites, epicycle wheel and a sun gear mounted on the secondary shaft, primary, secondary shaft of the gearbox output shaft carrier and output shaft Assembly are aligned, drove and case epicycle wheel have adjacent sprockets tubular shaft housing epicycle wheel, an output shaft carrier and output shaft Assembly are adjacent sprockets on the ring gear of the output shaft Assembly is installed, the clutch switch, which plug switching vzaimosvaz is on the slide, gear on the primary shaft is fixed, it is engaged with the gear, with gear extended, loosely mounted on the intermediate shaft, the gear output shaft also has a gear extended next to a ring gear of the primary gear shaft, these toothed crowns is the coupling gear interconnected with a fork switch with another coupling half mounted on the toothed crowns of the intermediate gear shaft, gear output shaft drove off, gear output shaft Assembly position, the clutch switch on the crown has three internal gear on the slide clutch switch is rigidly fixed gear with internal and external toothing, the external toothing of which is connected with the three-position ring gear housing of the planetary mechanism.
Gear freely mounted on the primary shaft, had an increased diameter, it limited the range of the gear ratio shaft of the gearbox, increased volume and intensity due to growth center distances. The planetary mechanism (PM) gearbox prototype provided three modes, but not in the optimal mode, when switching from low gear into reverse it is necessary to pass through the position of the higher gear; desperatley gear needed two coupling a movable connection between them.
The proposed solution allows to reduce size and metal shaft of the gearbox by combining gear with the primary shaft, to simplify the gear through the use of the ring gear with internal and external toothing instead of the clutch switch and implement three modes of the PM to the optimal mode switching gears: I-Uh ab=- ; II-Ub ah=To+1; III-U(bh)=1 when setting the dip of the ring gear of the output shaft carrier and the three-position of the ring gear and output shaft Assembly.
Figure 1 shows a diagram KP, figure 2 - radial chart and table position clutch switch at different speeds forward (top) and reverse (bottom).
Vertical beam corresponds to the transmission number equal to one. The greater the tilt of the beam, the higher the value of the gear ratio. In logarithmic scale, the slope of the beam is constant on any part of the radiation diagram. Rays of pairs of external gears gearing marked I, II, III, and rays characterizing the modes of operation of the planetary mechanism, - U=1,0; Ub ahand Uh ab.
In support of the unit's casing 1 are coaxially arranged input shaft 2, the output shaft 3, the output shaft carrier 4 and the output shaft Assembly 5. In parallel, they installed the intermediate shaft 6, on which oterom freely mounted gear 7 and is fixed to the gear train external gearing 8 and 9. These gears are vzaimozachety respectively with gears external gearing 10, 11 and 12, the gear 10 is fixed on the primary shaft 2 (made at the same time with him), gears 11 and 12 are freely mounted on the secondary shaft 3. On the secondary shaft 3 fixed sun gear 13, which is geared with satellites 14, mounted on the axes of the carrier 15 and meshed with epicycle wheel 16. The tubular shaft 17 case epicycle wheel 16 is connected with constitutive ring gear 18. On the output shaft drove a 4 next to the ring gear 18 mounted two-position crown gear 19. On the output shaft of the unit 5, near the toothed rims 18 and 19 fixed three-position crown gear 20. On the outer surface of the shell epicycle wheel 16 is crown gear 21. Next to the ring gear 21 is ring gear 22 of the carrier 15. Three-position crown gear 23 fixed to the body unit 1 opposite the gear rims 21 and 22. Clutch switch (A) consists of two coupling halves 24 and 25 connected by a fork switch 26, they are installed respectively between the gears 10-11 and 7-8. The clutch 27 (C) is installed on the hub of the output shaft 3 between the gears 11 and 12. The coupler (S) 28 is located on the ring gear 20 of the output shaft Assembly 5. Plug switch 29 slide 30 movably connected to the clutch switch 28 at the inner end of the slide is 30 fixed gear 31 with internal and external links.
The work of the KP as follows:
The first transmission
Clutch switch As In(27) are in the right position (P) - (see figure 2, table top right), clutch switch (28) is in the middle position (II). In this case (see figure 1) coupling And the coupling 25 connects the gear 7 gear 8 of the intermediate shaft 6, the coupling 24 is located on the toothed crown gear 11 and the output shaft 3 and not connect it with the primary shaft 2, the clutch connects the gear 12 with the secondary shaft 3, the clutch (28) connect (see figure 1 bottom right) ring gear 19 of the output shaft carrier 4 with a ring gear 20 of the output shaft of the unit 5, the fork switch 29, the slider 30 and the ring gear 31 connects the ring gear 23 of the housing unit 1 with a ring gear 21 and stops epicycle wheel 16 (b) relative to the body unit 1. The planetary mechanism (PM) is the mode with the ratio Ub ah=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 variants PM it is equal to 3, and the gear ratio GR is 4.
Torque from the primary shaft 2 gear 10 is transmitted to the sixth is Erny 7 (a pair of gears (I) the coupling 25 on the toothed crown gear 8 and the intermediate shaft 6, the gear 9 on the gear 12 (a pair of gears III). From the gear 12 by the coupling switch In (27) the torque is transmitted to the output shaft 3 and the sun gear 13. The sun gear 13 rotates the satellites 14, which objetivas stopped by the epicycle wheel 16, and transmit the increased torque on the carrier 15, the output shaft carrier 4, the gear 19, the clutch switch With (28), ring gear 20 and the output shaft Assembly 5.
Radiation diagram of this transfer correspond to the three series-connected beam: t to medium scale left (see figure 2) beam I go down to the right, then the beam III right up and then the gentle beam (Ub ab=To+1) to 1 on the right side of the scale.
A second pass
Move the clutch And in the left position, a pair of gears I turned off from work, because the coupling 25 divides the gears 7 and 8, includes a pair of gears II.
Torque from the primary shaft 2 is transmitted to the coupling 24 to the gear 11, next to the gear 8, then, as on a previous pass. Radiation diagram of this transfer also correspond to the three beam, but instead of I beam presents the beam II.
Change the position of the clutches and clutch And returns to the position corresponding to the first gear and the clutch connects with the secondary shaft 3 gear 11.
To the intermediate gear shaft torque PE udaetsya, as in first gear, then a pair of gears II (8-11), the coupling 27 on the output shaft 3, then, as in the previous transmission.
Radiation diagram of this transfer correspond to rays I, II and Ub ahdirected from t to v.3.
The fourth transfer
Move the clutch And to the left position, both clutches are connected with the gear 11.
Torque from the primary shaft 2 is transmitted to the output shaft 3 directly on the coupling 24, the gear 11 and the clutch 27, and then, as in the previous transmission.
Radiation diagram of this transfer corresponds to one ray Ub ahdirected from t to v.4.
The fifth transmission
Return couplings a and b in the state corresponding to the first transmission, and clutch to be moved to position III. Crown gear 31 extends from a connection with a ring gear 21 of the housing epicycle wheel 16 is in the off position, the clutch 28 left and middle inner crowns connects the right side of the ring gear 19 of the carrier 15 with a ring gear 18 epicycle wheel 16. 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 jagged veins of the AMI 18 and 19, clutch switch 28 on the ring gear 20 and the output shaft Assembly 5.
Radiation diagram this transmission is represented by three rays: two first beam I and III correspond to the first gear and the third beam is directed vertically upwards to V.5.
The sixth transmission
Switchable coupling And to the left position.
Torque to PM is passed as the second gear, and then - as the previous one.
Radiation diagram of this transfer correspond to rays II, III and U=1,0.
The seventh transmission
Change the position of the couplings a and b in 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 I beam tilted to the right, down and rays II and U=1,0 characterize this transfer.
The eighth transmission - direct
Move the clutch And left.
To PM the torque is transmitted, as in fourth gear, then as in the last three transmission.
Radiation diagram this transmission is represented by one vertical beam U=1,0 from t to 8.
Reverse gears are provided with the PM when switching the clutch in position I - gear 31 from the clutch connects the ring gear 22 of the carrier 15 with the ring gear 23 of the housing unit 1 and stops the carrier sleeve 28 secondary ring gear (see figure 1 top right) connects the ring gear 18 epicycle what about the wheels 16 with the ring gear 20 of the output shaft Assembly 5. PM works in mode Uh ab=-To, a sun gear 13 satellites 14, mounted on the axis is stopped drove 15, slowly rotates the epicycle wheel 16 and the output shaft Assembly 5 in the opposite direction.
The first back - 1R
Install couplings a and b in the position of the first gear and the clutch is in position I (see figure 2, below right).
To PM the torque is transmitted, as in the first forward gear, then from the sun gear 13 satellites 14 on the epicycle wheel 16, then through the tubular shaft 17, a toothed crown 18, the clutch 28, a toothed crown 20 to the output shaft of the unit 5.
Radiation diagram, the reverse gear is represented by three rays: I, III, and Uh ab=-From t to .1R.
The second back - 2R
Switchable coupling And to the left position.
Torque to PM is passed as the second forward gear, then, as on a previous pass.
Radiation diagram of this transfer correspond to the three beam: II, III, and Uh ab=-K.
The third back - 3R
Change the position of the clutches a and B.
Until PM torque is supplied as the third forward gear, then, as in the last two gears.
Radiation chart, the three beams I, II and Uh ab=-To characterize this transfer.
The fourth is the first back - 4R
Move the clutch And to the left position.
To PM the torque is transmitted directly, as in the fourth forward gear, then, as on the last transmission.
Gentle beam Uh ab=-From t to T.4R is this transfer.
When you change the settings of the external gears of the gearing and PM distribution transmission and skew rays will also change.
Coaxial spread-planetary transmission, comprising a housing unit in which there are three coaxial gearbox with three pairs of vzaimozachetnykh gear outer gear, the two gears on the intermediate shaft are combined in a block, gears on the secondary shaft of the gearbox is installed freely between them is a clutch gear, the output gear is a simple three planetary gear with planet carrier, satellites, epicycle wheel and a sun gear mounted on the secondary shaft, primary, secondary shaft of the gearbox output shaft carrier and output shaft Assembly are aligned, drove and case epicycle wheel are adjacent sprockets, a tubular shaft housing epicycle wheel, an output shaft carrier and output shaft Assembly are adjacent sprockets on the ring gear of the output shaft of the unit set the coupling switch to ora plug switch interconnected with the slide, characterized in that the gear on the primary shaft is fixed, it is engaged with the gear, with gear extended, loosely mounted on the intermediate shaft, the gear output shaft also has a gear extended next to a ring gear of the primary gear shaft, these toothed crowns is the coupling gear interconnected with a fork switch with another coupling half mounted on the toothed crowns of the intermediate gear shaft, gear output shaft drove off, gear output shaft Assembly position, the clutch switch on the crown has three internal gear on the slide clutch switch rigidly fixed ring gear with internal and external toothing, the external toothing of which is connected with the three-position ring gear housing Assembly.
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.
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.
EFFECT: possibility of using driving shaft on tractor-cultivator without changing design of load-bearing frame of standard tractor-cultivator with preservation of performance characteristics of said tractor-cultivator.
39 cl, 15 dwg
FIELD: transport engineering.
SUBSTANCE: proposed wheel has rim of regular shape and center of rotation. To drive the wheel, planetary reduction gear is fitted in wheel rim whose drive gear is planet pinion installed on driving "floating shaft whose axis, taking weight of vehicle applied to wheel, executes complex movement relative to axis of wheel rotation making it possible to: 1) spread projections of axis of rotation (being simultaneously point/line of support) of wheel and point of application of vehicle weight P to wheel on horizontal surface by some distance L; 2) change position of projection of point P on vertical; plane by some height h and provide constantly acting "canting" torque PL on wheel creating effect of eccentric wheel at wheel circumference remaining unchanged and eliminating cyclic loads.
EFFECT: improved cross-country capacity of vehicle, its steerability, efficiency of wheeled propulsor, simplified design.
FIELD: transport engineering.
SUBSTANCE: invention relates to drives of all-wheel-drive cross-country vehicles designed for riding along roads and off-road. Proposed two-step planetary transfer case contains upper planetary reduction gear providing two speeds of transfer case, intermediate shaft with gear 5 and lower planetary reduction gear being essentially differential drive for rear and front driving axles. Driving member of upper planetary reduction gear is crown gear 9 stationary connected with drive shaft 8, driven member is carrier 13 and controlled member is central gear 11. Gears of upper planetary reduction gear, driving gear 4, intermediate gear 5 and driven gear 6 and gears of lower differential mechanism are arranged in one row one over the other.
EFFECT: reduced overall dimensions adapted for mounting transfer case on vehicles.
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.
EFFECT: improved design.
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.
EFFECT: enlarged operating capabilities of vehicle.
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.
EFFECT: improved operating capabilities of vehicle owing to optimum distribution of gears over range, improved gearshift mechanism and reduced metal usage of set.
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.
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.
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.
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.
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.
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: automotive industry.
SUBSTANCE: proposed gearbox contains great number of gears forming step up and down stages. Each set is formed by transmission gear fixed on shaft and installed for connection with shaft through sliding gear. Each end outlet mechanism is firmed by end outlet member (101, 102, 103, 104 - which are clutches) and connected with it by shifter fork (105, 106, 107, 108). Shifter forks (105, 106, 107, 108) are arranged on shaft 109 for axial travel. Transmission stages are engaged by connecting sliding gear with carrying shaft by means of end outlet member (101, 102, 103, 104). End outlet mechanism is set into action by end actuating mechanism. Sequence of speed changing is not set in end actuating mechanism. End actuating mechanism contains at least one main actuating member III - shifter pin, which comes into active engagement with end outlet members 101, 102, 103, 104. Possibility of engagement of one transfer stage by means of first end outlet mechanism is provided. And then at least one main actuating member can come into active engagement with other end mechanism without disengagement of stage preliminarily shifted in. Each actuating mechanism contains at least one auxiliary actuating member (113, 116, -thin cams). Description of automobile with such gearbox is provided. Proposed invention provides gearbox in which sequence of speed changing in end actuating mechanism is not set, time of speed changing is considerably reduced and safety is increased.
EFFECT: simple design of gearbox with minimum possible number of parts, ease of control without additional safety precautions.
68 cl, 44 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.