Sixteen-stage coaxial planetary gearbox 16r4 with dual clutch

FIELD: transport.

SUBSTANCE: dual clutch is arranged at gearbox input with portion of clutch driven discs fitted at primary shaft and another portion fitted at tubular shaft. Gears engaged with countershaft gears are fitted on said shafts. Countershaft carries six gears, two being engaged with gears fitted on secondary shaft. Three-position clutch with reverse driven gear is arranged there between. Gear engaged with countershaft gear and three-position shift collar are fitted on countershaft tubular extension 8. Simple three-link planetary mechanism and three position clutch 35 is arranged at gearbox output side.

EFFECT: enhanced performances, higher flotation and perfected control.

2 dwg

 

The invention relates to vehicle engineering, powertrain vehicles.

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

These units are structurally complex and bulky.

Closest to the proposed 16-Testamental gearbox, a gearbox according to the patent RU No. 2419007 C1 (bull. No. 14 of 20.05.20011).

Valvoplasty transmission 12R4 the patent RU No. 2419007 consists of a main 6-Testamental KP and two simple three-tier PM (planetary gear). 8 gears for speeds forward, 4 reverse gear and three clutch switch (one of them double) main gearbox and a three-level PM (sun gear, epicycle wheel and drove with satellites) with the clutch switch provides 12 speeds forward and 4 reverse gears.

The drawbacks of the transmission unit are to limit the operational characteristics of the vehicle when shifting gears with breaking the flow of power, insufficient number of gears and the range of KP (p is redatory numbers lower and higher gears). As a rule, modern trunk cars-trucks have 16 gears with a range of about 17.

The problem to which the invention is directed, is to expand the operational capabilities of the vehicle due to the pairwise shift almost without breaking the flow of power, increasing the number of gears and the range of KP, increasing the durability of the gearbox by reducing the length of the shaft.

The problem is solved at the expense of achieving a technical result, which is in the process of shifting through the installation of a dual clutch, and also by increasing the number of gears and the range gearbox, improved durability gearbox by increasing the rigidity of the shaft while reducing their length.

The essence of the proposed device is that, such as: valvoplasty transmission includes a housing main gearbox, it supports are parallel shafts on which are installed a pair of external gears of the gear on the secondary shaft, between two loosely mounted gears, is a three-position clutch switch and fixed tubular tip supported in the inner wall of the transmission housing, this tip is bearing shaft, the tip of the NWO is one gear set, meshed with the gear of the intermediate shaft, three-position clutch switch is located next to the gear shaft in the casing of the planetary gear is a sun gear mounted on the secondary shaft, through satellites drove it meshed with epicycle wheel, the output tubular shaft of the wheels are three-position clutch switch, while, unlike the prototype, on the intermediate shaft all six gears fixed on the entrance to the gearbox in case there is an input shaft with a fixed housing of the dual clutch with top drives on the primary shaft installed the slave drives the left clutch, between them and the gear, fixed on this shaft is freely tubular shaft that has driven disks of the right clutch and fixed gear, gear primary and tubular shaft meshed with the intermediate gear shaft, driven gear, reverse gear is positioned on the clutch switching output shaft, an additional reverse gear mounted on an axis located between the intermediate and secondary shafts.

The proposed solution allows a dual clutch in pairs to switch gears (16 and 15, 14 and 13, 12 and 11, and so on) almost without breaking the flow of power that facilitates the management process Tran is tailor product and increases its permeability, an additional pair of gears allows you to increase the number of gears and the range of MCP (multi-stage gearbox). The inner wall of the housing main gearbox increases the rigidity of the Assembly and durability of MCP by increasing the stiffness of the shafts while reducing their length.

In Fig.1 shows a kinematic diagram of the 16-Testamental spread-planetary MCP 16R4 (16 speeds forward and 4 reverse) with dual clutch, consisting of three main pine KP and simple three PM. In the lower part (under Fig.1) denotes the number of pairs of gears (1P-5P) and gears reverse gear R.

In Fig.2 shows a radiation diagram MCP 16R4 tables provisions clutches and couplings switch to a different transmission. In the top row of the table shows the number included pairs of gears and PM (planetary mechanism in the condition U=K+1, where K is an internal parameter PM is equal to the ratio of the number of teeth of the epicycle wheel to the number of teeth of the sun gear). On the horizontal scale of the chart in logarithmic form presents the values of the ratios of pairs of gears and gear. Above the upper horizontal designated number of speeds forward (16-1), on the penultimate horizontal - reverse gear (4R-1R). On the upper horizontal and the penultimate horizontal right size gear ratios refer to output the resultant shaft, associated with the planet carrier PM; on the second rank to the secondary shaft, on the penultimate horizontal left - to intermediate shaft. Included pairs of gears are on the rays. The inclination of the beam to the right indicates a decelerating mode of operation of the pair of gears than the provisions of the beam, the greater the gear ratio. The inclination of the beam to the left, 2P - to 16-th transmission, 3P - to 14-th and 13-th transmission, characterized by the accelerating mode of the pair of gears. The tilt of the beam of each pair of gears is constant on any part of the radiation diagram.

The proposed device consists of a casing main CP 1 with the inner wall 2, the housing of the dual clutch 3 and the housing 4 PM (planetary gear), in their bearings are coaxially arranged input 5 and primary 6 shafts and the output shaft 7 with a tubular tip 8 and the output shaft 9. On the primary shaft 6 freely mounted tubular shaft 10. The intermediate shaft 11 with the PTO (PTO) is parallel to the shafts 5-9. Gear 12-17 rigidly mounted on the intermediate shaft 11. Gear 12 meshed with the gear 18 which is fixed on the tubular shaft 10. Gear 13 meshed with the gear 19 fixed on the primary shaft 6. Gear 14 meshed with the gear 20, which is freely mounted on the tubular tip 8 of the secondary shaft 7. Gears 15 and 16 are meshed with the gears 21 and 22, which are freely mounted on the secondary valu. On tubular tip 8 between the gears 19 and 20 is a three-position clutch 23 (a). Three-position clutch 24 (C) of the secondary shaft 7 is located between the gears 21 and 22. Slave reverse gear 25 fixed on the three-position clutch 24 in the neutral position is located opposite the leading reverse gear 17 fixed on the intermediate shaft 11 between the gears 15 and 16. Additional reverse gear 26 mounted on an axis 27 which is located between the intermediate 11 and secondary shafts 7. On the input shaft 5 is fixed to the casing 28 of the dual clutch, there are wheel rims 29 of the clutch. Driven disks 30 of the left grip (L) are mounted on the primary shaft 6 and driven disks 31 of the right clutch (P) are mounted on the tubular shaft 10. The control device which presses the driving and the driven disks when turning on the clutches, not shown. The output of the secondary shaft 7 is fixed sun gear 32 (a), which satellites 33 led 34 (h) geared with epicycle wheel 35 (b) PM. Carrier 34 is fixed to the output shaft 9. The output tubular shaft 36 epicycle wheel 35 between the gear rims of the housing 4 PM and the output shaft 9 mounted three-position clutch switch 37 PM (C).

Between the input shaft 5 and the housing 28 dual clutch it is possible to install gears (cylindrical, codices is Oh, hypoid and so on).

KP works as follows: the dual clutch fires whenever the switch, which occurs almost without breaking the flow of power. Clutch And changes its position after the two switches, the clutch - after four consecutive shifts, and coupling - after eight consecutive shifts. PM (planetary gear) provides two modes: eight lower gear (1-8) epicycle wheel 35 is stopped relative to the housing 4 PM clutch 37 (C) in the left position and provides a gear ratio U=K+1, the eight highest gear (9-16) epicycle wheel 35 and the carrier 34 is connected by a coupling 37 (C) in the right position, PM blocked and provides a gear ratio U=1.

The first transmission

Include the left grip (L) coupling And (23) in the neutral position (N), the clutch (24) in the right (P), and coupling (37) in the left (L) (see Fig.2, the upper table over so-1). Included 2nd and 5th pair of gears and PM in mode U=K+1.

Torque from the left clutch (L) is transmitted to the input shaft 6, a pair of gears 19-13, on the intermediate shaft 11, a pair of gears 16-22, sleeve (24) on the secondary shaft 7, the sun gear 32. Satellites 33, objetivas stopped by the epicycle wheel 35, rotate carrier 36 and the output shaft 9 at a low speed and high torque.

On the beam of the ow diagram (see Fig.2) this program presents three rays: from 0 so the second horizontal flat beam 2P right down to the third horizontal line, then a gentle beam 5P right up to the second rank, then the gentle beam PM to 1 on the upper horizontal line.

A second pass

Include the right grip (P), the other clutches in the same position. Turn off the 2nd pair of gears included the 1st couple of gears.

Torque from the right clutch (P) is transmitted to the tubular shaft 10, a pair of gears 18-12 on the intermediate shaft 11, hereinafter referred to as first gear.

Radiation diagram (see Fig.2) this program presents three rays: from 0 so the second horizontal steep beam 1P right down to the third horizontal line, then a gentle beam 5P right up to the second rank, then the gentle beam PM to 2 on the upper horizontal line.

Third gear

Clutch, clutch a and C, as in first gear, the clutch switch in the left position (L). Included 2nd and 4th pairs of gears and PM in mode U=K+1.

Torque, as in first gear on the primary shaft 6 is transmitted by a pair of gears 19-13 on the intermediate shaft 11, a further pair of gears 15-21, sleeve (24) in the left position on the secondary shaft 7, hereinafter referred to as the first transmission.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal flat beam 2P right down to the third g is rizontal, next steep beam 4P right up to the second rank, then the gentle beam PM to 3 on the upper horizontal line.

The fourth transfer

Include the right grip (P), the other clutches in the same position. Included 1st and 4th pairs of gears and PM in mode U=K+1.

From the right clutch torque, as in second gear is transmitted to the intermediate shaft 11, hereinafter referred to as third gear.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal steep beam 1P right down to the third horizontal line, then a rapid ray 4P right up to the second rank, then the gentle beam PM to 4 on the upper horizontal line.

The fifth transmission

Include the left grip (L), the clutch And switch in the right position (P), and the clutch is in neutral (N). Included 2nd and 3rd pairs of gears and PM in mode U=K+1.

As in the first and third gears, the torque is transmitted to the intermediate shaft 11, a further pair of gears 14-20, coupling And (23) on the tip 8, the output shaft 7, PW-mode, U=K+1 and the output shaft 9.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal beam 2P right down to the third horizontal line, then a rapid beam 3P left up to the second rank, then the gentle beam PM to 5 on the upper horizontal line.

The sixth transmission

Include the right grip (P), ostalnymi in the same position. Included 1st and 3rd pairs of gears and PM in mode U=K+1.

As on the second and fourth gears, the torque is transmitted to the intermediate shaft 11, hereinafter referred to as a previous pass.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal beam 1P right down to the third horizontal line, then a rapid beam 3P left up to the second rank, then the gentle beam PM to 6 on the upper horizontal line.

The seventh transmission

Include the left grip (L), the other clutches in the same position. Included direct transmission in the main CP and PM in mode U=K+1.

The torque is transmitted from the primary shaft 6 of the clutch 23 (a) on the tip 8, the output shaft 7, hereinafter referred to as a previous pass.

Radiation diagram this transmission is represented by a single ray: so 0 on the second rank is the most gentle beam PM to 7 on the upper horizontal line.

The eighth transmission

Include the right grip (P), the other clutches in the same position. Included 1st and 2nd pairs of gears and PM in mode U=K+1.

As to the second, fourth and sixth gears, the torque is transmitted to the intermediate shaft 11, a further pair of gears 13-19, then as in the previous transmission.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal beam 1P right down to the third horizontal line, then a gentle beam 2P left up vtoroy horizontal, then the gentle beam PM to 8 on the upper horizontal line.

The ninth transmission

Switchable clutch in the right position (P), the rest of the clutch in the position of the first transmission. Included 2nd and 5th pair of gears and PM in mode U=1.

Torque to the sun gear 32 is transmitted as the first transmission, then blocked PM and drove 36 on the output shaft 9.

Radiation diagram (see Fig.2) this program presents three rays: from 0 so the second horizontal flat beam 2P right down to the third horizontal line, then a gentle beam 5P right up to the second horizontal, vertical beam PM to 9 on the upper horizontal line.

The tenth transmission

Include the right grip (P), the other clutches in the same position. Turn off the 2nd pair of gears included the 1st couple of gears.

Torque to PM is transmitted on the second transmission, hereinafter referred to as ninth transfer.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal steep beam 1P right down to the third horizontal line, then a gentle beam 5P right up to the second horizontal, then vertical beam PM to 10 on the upper horizontal line.

The eleventh transmission

The clutch in the right position (P), the rest of the clutch in the position of the third transmission. Included 2nd and 4th pairs of gears and PM in mode U=1.

Torque to PM is sent, as Tr is the article transfer, hereinafter referred to as the tenth transfer.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal flat beam 2P right down to the third horizontal line, then a rapid ray 4P right up to the second horizontal, then vertical beam PM to 11 on the upper horizontal line.

The twelfth transmission

Include the right grip (P), the other clutches in the same position. Included 1st and 4th pairs of gears and PM in mode U=1.

Torque to PM is passed as fourth gear, then as in the previous transmission.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal steep beam 1P right down to the third horizontal line, then a rapid ray 4P right up to the second horizontal, then vertical beam PM to 12 on the upper horizontal line.

The thirteenth transmission

The clutch in the right position (P), the rest of the clutch in the position of fifth gear. Included 2nd and 3rd pairs of gears and PM in mode U=1.

As to the fifth gear, the torque is transmitted to the PM, which is in mode U=1, and then to the output shaft 9.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal beam 2P right down to the third horizontal line, then a rapid beam 3P left up to the second horizontal, then vertical beam PM to 13 on the upper horizontal line.

Chetyrnadcat the second transfer

Include the right grip (P), the other clutches in the same position. Included 1st and 3rd pairs of gears and PM in mode U=1.

As to the sixth gear, the torque is transmitted to the PM, then as in the previous transmission.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal beam 1P right down to the third horizontal line, then a rapid beam 3P left up to the second horizontal, then vertical beam PM to 14 on the upper horizontal line.

The fifteenth transmission - direct

Include the left grip (L) and the clutch And to the left (L), the other clutches in the same position. Included direct transmission in the main CP and PM in mode U=1.

The torque is transmitted from the primary shaft 6 of the clutch 23 (a) on the tip 8, the output shaft 7, hereinafter referred to as a previous pass.

Radiation diagram this transmission is represented by a single ray from 0 so the second horizontal vertical beam PM to 15 on the upper horizontal line.

Sixteenth transfer

Include the right grip (P), the other clutches in the same position. Included 1st and 2nd pairs of gears and PM in mode U=1.

As the eighth gear, the torque is transmitted on the PW, then as in the previous transmission.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal beam 1P right down to the third horizontal line, then cool the beam 3P left up to the second rank, then the vertical beam PM to 16 on the upper horizontal line.

The first back - 1R

Include the left grip (L), clutch And switched to the neutral position (N), as at the first, third and fifth gears, the clutch is in neutral position (N), an additional reverse gear 26 is introduced into engagement with the leads 17 and driven gears 25 reverse clutch (37) in the left (L) position.

The torque to the intermediate shaft 11 is supplied as the first forward gear, then a series of gears 17-26-25 reverse clutch (24) on the secondary shaft 7, the sun gear 32, 33 satellites, objetivas stopped by the epicycle wheel 35, rotate carrier 36 and the output shaft 9 at a low speed and high torque in a direction opposite to the rotation of the input shaft 5.

Radiation diagram (see Fig.2 below) this transmission is represented by three rays: from 0 so the second horizontal flat beam 2P right down to the third horizontal line, then a gentle beam R to right down to the bottom horizontal, then the gentle beam PM t 1 R on the third horizontal line.

The second back - 2R

Include the right grip (P), the other clutches in the same position. Turn off the 2nd pair of gears included the 1st couple of gears.

The torque to the intermediate shaft 11 is supplied as the second forward gear, hereinafter referred to as the first and reverse gear.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal steep beam 1P right down to the third horizontal line, then a gentle beam R to right down to the bottom horizontal, then the gentle beam PM t 2 R on the third horizontal line.

The third back - 3R

Include the left grip (L), the clutch is in the right position (P), the other clutches in the transmission 1R.

The torque to the intermediate shaft 11 is supplied, as in the first reverse gear, then the number of gears 17-26-25 reverse clutch (24) on the secondary shaft 7, the sun gear 32, goods receipt blocked stock, rotate carrier 34 and the output shaft 9.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal flat beam 2P right down to the third horizontal line, then a gentle beam R to right down to the bottom horizontal, then vertical beam PM t 3 R on the third horizontal line.

Fourth reverse - 4R

Include the right grip (P), other couplings remain in the same position.

The torque to the intermediate shaft 11 is supplied as the twelfth forward gear, hereinafter referred to as a previous pass.

Radiation diagram this transmission is represented by three rays: from 0 so the second horizontal flat beam 1P right down to the third horizontal line, then a gentle beam R to right down to the bottom of Gori is antali, then the vertical beam PM t 4 R on the third horizontal line.

If you take most often used in MCP (multi-stage transmission) interval - ratio gear ratios adjacent gear - q=1,21, you get a range of D=17,45; value ratios of pairs of gears: first - 1,44; the second and fifth - 1,77; third and fourth - 1,21. The gear ratio GR will be 4,59; internal parameter PM is equal to the ratio of the number of teeth of the epicycle wheel to the number of teeth of the sun gear will be 3,59 (calculations provided between the contour lines in Fig.2).

The proposed MCP has a good layout features: small size ratios of pairs of gears, which provides the possibility of reducing the axle spacing and dimensions of the MCP; the main increase in torque occurs in PM, 8 intervals of 15, which unloads the main CP. PM is an internal parameter that is close to optimal, is not more than 5.

Designation

1 - corps main CP,

2 - the internal wall of the housing KP

3 - body dual clutch

4 - case PM (planetary gear),

5 - input shaft

6 - primary shaft

7 - a secondary shaft,

8 is a tubular tip of the output shaft 6,

9 - output shaft from the carrier PM

10 is a tubular shaft,

11 - intermediate shaft,

12-17 - pinion fixed on the intermediate shaft 11,

p> 18 - gear tubular shaft 10,

19 is a gear fixed on the primary shaft 6,

20 is a gear freely mounted on the tubular tip 8 of the secondary shaft 7,

21, 22 - gear freely mounted on the secondary shaft 7,

23 (A) three-position coupling the tubular tip 8, located between the gears 19 and 20,

24 (B) - three-position coupling the output shaft 7 located between the gears 21 and 22,

25 - ring reverse gear mounted on the sleeve 24 (B)

26 is an additional reverse gear mounted on the axis 27,

27 - axle additional reverse gear 26,

28 - housing of the dual clutch

29 - wheel clutch 28,

30 - driven disks of the left (L) clutch 28, mounted on the primary shaft 6,

31 - driven disks right (P) clutch 28 mounted on the tubular shaft 10,

32 is a sun gear of the PM

33 satellite carrier 34,

34 - carrier PM

35 - epicycle wheel PM

36 is a tubular shaft epicycle wheel 35,

37 (S) - three-position clutch PM, located between the toothed rims of the housing 4 PM and the output shaft 9.

Such as: valvoplasty transmission, comprising a housing main gearbox, it supports are parallel shafts on which are installed a pair of external gears of the gearing, secondary is m shaft, between two loosely mounted gears, is a three-position clutch switch and fixed tubular tip supported in the inner wall of the transmission housing, this tip is bearing shaft, the tip of the loosely mounted gear, meshed with the gear of the intermediate shaft, three-position clutch switch is located next to the gear shaft in the casing of the planetary gear is a sun gear mounted on the secondary shaft, through satellites drove it meshed with epicycle wheel, the output tubular shaft of the wheels are three-position clutch switch, characterized in that the intermediate shaft all six gears fixed at the entrance to the gearbox in case there is an input shaft with a fixed housing of the dual clutch with top drives on the primary shaft installed the slave drives the left clutch, between them and the gear fixed on this shaft is freely tubular shaft that has driven disks of the right clutch and fixed gear, gear primary and tubular shaft meshed with the intermediate gear shaft, driven gear, reverse gear is positioned on the clutch switching output shaft, an additional reverse gear is recovered from the axis, located between the intermediate and secondary shafts.



 

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SUBSTANCE: invention relates to vehicle planetary gearboxes. Automatic gearbox executes nine forward gears and one rear gear comprises crankcase (19), input link (20), output link (21), hydromechanical torque converter and planetary reduction gear. This reduction gear comprises four planetary rows, three controlled clutches and three controlled brakes. First row consists of sun gear (3), carrier (2) and crown gear (1). Second row consists of sun gear (6), carrier (5) and crown gear (4). Third row consists of sun gear (9), carrier (8) and crown gear (7). Fourth row consists of sun gear (12), carrier (11) and crown gear (10). Input link (20) engages with output link of hydromechanical torque converter (22), first planetary row sun gear (3) and second planetary row sun gear (6). Output link (21) engages with fourth planetary row crown gear (10). First planetary row crown gear (1) engages with third planetary row carrier (8). Brake (13) couples first planetary row carrier (2) with crankcase of gearbox (19). Brake (14) couples third planetary row carrier (9) with crankcase of gearbox (19). Brake (15) engages engaged fourth planetary row carrier (11) and second planetary row crown gear (4) with gearbox crankcase (19). Clutch (16) engages first planetary row carrier (2) with engaged third planetary row crown gear (7) and fourth planetary row sun gear (12). Clutch (17) engages second planetary row carrier (5) with engaged fourth planetary row crown gear (10) and output link (21). Clutch (18) engages third planetary row carrier (5) with engaged second planetary row crown gear (4) and fourth planetary row carrier (11).

EFFECT: increased number of gears.

1 dwg

Gearbox // 2531995

FIELD: transport.

SUBSTANCE: invention relates to gearboxes. Gearbox comprises fixed housing, input and output differentials. Every said differential consists of interacting links: sun gear, epicycle, carrier with pinions, input link engaged with input differential sun gear, output link engaged with output differential carrier, gears, controlled clutches, shafts engaged with differential links and articulation between shafts to be thrown in by controlled clutches. Besides, gearbox comprises idler wheel and controlled interlocking clutches for engagement of epicycle with input differential carrier and epicycle with output differential sun gear. This gearbox allows thirteen different speeds of output link revolution on one direction and two speeds in opposite direction.

EFFECT: high efficiency and wide range of gear ratio, reduced metal input.

4 cl, 4 dwg, 1 tbl

FIELD: transport.

SUBSTANCE: group of invention relates to versions of bicycle design and belt drive system. Bicycle comprises the frame and at least one wheel secured to said frame. Wheel has hub, second planetary gearbox arranged therein and belt for torque transmission between first planetary gearbox and second planetary gearbox. In compliance with first version, this frame comprises receiver to accommodate said first planetary gearbox. In compliance with second version, this frame also comprises receiver to accommodate said first planetary gearbox of different design version. In compliance with first version, belt drive system comprises frame, receiver, first planetary gearbox located therein and second planetary gearbox located in wheel hub. In compliance with second version, belt drive system comprises first planetary gearbox arranged in first receiver and second planetary gearbox arranged in second receiver.

EFFECT: decreased weight, better frame clearance.

15 cl, 30 dwg

FIELD: transport.

SUBSTANCE: invention relates to modular A/T. Modular gearbox has planetary system composed of universal range differential wherein spider (5) with three pairs of engaged three-rim pinions is shared by 1st, 2nd and 3rd rows spider, 1st planetary row crown wheel, 2nd row crown wheel and 3rd row central sun gear are engaged by friction brakes with gearbox crankcase. Crown wheel makes an output link of gearbox. Said A/T universal range differential and extra planetary rows allows various design versions.

EFFECT: higher efficiency of gearbox.s

6 cl, 6 dwg

FIELD: physics.

SUBSTANCE: planetary mechanism comprises a photometer consisting of a disc (1), which is equipped with an axle (2), having openings that are equidistant from each other and from the centre of the disc, in which light filters are located. The axle (2) interacts with the disc through a free-wheel clutch (3). In the openings of the disc there are rotatable adapters (4), the outer surface of which is in form of gear wheels which interact with a central gear wheel (5), immovably mounted on the axle (2). The disc interacts with the base through another free-wheel clutch (7). Directions of the working strokes of the free-wheel clutches (3, 7) are opposite.

EFFECT: along with the possibility of moving the light filters, the invention enables to turn each of the light filters about its own axis.

1 dwg

FIELD: automobile production.

SUBSTANCE: automatic gearbox has one planetary gear set (4) and a torque moment transfer route passing parallel to that planetary gear set (4). Planetary gear set (4) at one transmission stage of gearbox (1) is not used for torque moment transfer and is rotated without any relative number of revolutions of its components relative to each other. With that, at the above transmission stage, the structure of the connection of the same planetary gear set (4) has the possibility of being changed by means of coupling clutches (10,11) so that gear transmission ratio of planetary gear set (4) changes from gear transmission ratio of reduced transmission to gear transmission ratio of increased transmission, or vice versa.

EFFECT: simpler design of the device.

10 cl, 33 dwg

FIELD: machine building.

SUBSTANCE: gearbox includes a cylindrical helical planetary reduction gear, a carrier with satellites and their axes, a friction coupling, centrifugal weights on the coupling housing and an automatic control system of the state of a sun gear (locking, unlocking). Crown gear of planetary reduction gear is installed in a movable manner on a drive shaft, sun gear is installed freely. Carrier with satellites and their axes are fixed on a driven shaft. Drive disks of friction coupling are connected through splines to crown gear, and driven ones are connected through the coupling housing to the carrier. Automatic control system of the sun gear state includes a brake consisting of a pulley fixed on a hub of the sun gear, the brake band of which is connected through rods and two-arm levers with a spring to crown gear and two-arm control lever through a rod directly from the carrier. Gearbox has three modules so that driven shaft of the previous module is a drive shaft of the following one, which is installed after the last module of a reverse mechanism.

EFFECT: reduction of fatigability of a driver and accident risk; improving reliability of a friction coupling.

1 dwg

Automotive gearbox // 2486389

FIELD: transport.

SUBSTANCE: gearbox comprises planetary step-down helical gearbox and automatic system of shifting from 1st to 2nd gear. Said planetary reduction gear consists of drive shaft 1 supporting crown gear 2 with drive disc secured thereat, sun gear 3 running on driven shaft 4 with carrier 5 rigidly secured thereat with axles 6 and pinions 7 engaged with crown and sun gears. Automatic gear shifting system consists of friction coupling with its drive discs 8 coupled via splines with crown gear and driven discs coupled via case 10 and disc with pinion axles and carrier and with driven shaft of centrifugal weights 11 with springs 12, and automatic sun gear control system. Cases of coupling 10, disc 26 and axles of pinions 6 and carrier are rigidly interconnected. Extreme left drive disc of coupling 27 is bolted to crown gear. Slave arms of centrifugal weights with sleeves at their ends are pressed via working springs to crown gear for compression of coupling discs.

EFFECT: higher reliability.

1 dwg

FIELD: transport.

SUBSTANCE: invention relates to automotive industry and may be used in agricultural machinery and trackless machines. Proposed vehicle comprises body 2 to house two-stage planetary final drive 2 coupled via gearshift mechanism 3 with engine 4. Said planetary final drive 2 comprises two planetary trains 5. Planetary train 5 consists of carrier 6 with pinions 7 engaged with side brake 8, sun gear 9 and ring gear 11. Clutches of sun and ring gears locking and sun gear brakes are composed of inertial synchromesh units, each being engaged with sun gear of appropriate planetary train to be locked with ring gear or final drive housing.

EFFECT: higher reliability, reduced power loss in turns.

2 dwg

FIELD: transport.

SUBSTANCE: invention relates to vehicles and can be used in towing trucks, tractors, road-building and other machines. At the inlet of transmission dual clutch (3) is located. Part of driven disks (28) of this clutch is installed on the main drive shaft (5), and the other part (29) - on tubular shaft (8). On these shafts gears are mounted which are engaged with gears of intermediate shaft (9) on which six gears are mounted, two of which are engaged with gears (19, 20) freely mounted of the secondary shaft (6). Between them, three-position shift collar (22) with reverse driven gear (23). On the tubular tip (7) of the secondary shaft (6), the gear (18) is freely mounted which is engaged with the gear (12) of intermediate shaft (9), and three-position shift collar (21) is located.

EFFECT: invention is aimed to enhancement of operational and layout characteristics of a vehicle by means of improvement of its floatation and facilitation of control due to pairwise gear shifting by dual clutch virtually without power flow interruption, as well as due to increased range and durability of transmission because of increasing rigidity of shafts while decreasing their length.

2 dwg

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