Sixteen-speed misaligned shaft-and planetary gearbox

FIELD: transport engineering.

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

EFFECT: reduced metal usage, simplified design of gearbox.

2 dwg

 

The invention relates to transport machinery, transmission vehicles.

Closest to the offer, such as : a non-axial Volynoblenergo gearbox (KP) is a non-axial gearbox 16R8 (16 speeds forward and 8 reverse gears) patent RU NO. 2050290 UK 17/08 (20.12.95 bull. No. 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 KP compared to conventional KP traditional layout (four basic gearbox with front divides the LEM and the rear planetary demultiplier) has good structural characteristics, but for switching States of the planetary mechanism (PM) are two independent clutch switch, with three couplings switching shaft of the gearbox received patitofeo CP, which complicates the control of the transmission unit; two three-position clutch switch located inside shaft of the gearbox, which increases size and metal gearbox.

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

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

The achievement of the technical result is ensured by the fact that, such as : a non-axial valvoplasty transmission includes a housing placed in parallel the primary and secondary shafts, arranged them in four rows of pairs of meshed gears, two gears on each shaft are combined in blocks, 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 mounted on the toothed crown gear secondary shaft, the hub of the output shaft between the loosely mounted gears clutch is re what to do, the output of the secondary shaft fixed sun gear of the simple three planetary gear, carrier and housing epicycle wheels are sprockets located next to the ring gear housing, gear output shaft position, characterized in that the input shaft with the ring gear and installed the clutch switch is located coaxially to the primary shaft, which is fixed to gear, next to it is checked gear tubular shaft, which is fixed to the gear, meshed with the gear of the gear train output shaft, the second gear unit meshed with the gear fixed on the primary shaft, gear shaft drove off, the clutch switch on the gear output shaft has three internal gear on the slide clutch switch is rigidly fixed ring gear with internal and external links, external toothing of which is connected with the three-position ring gear housing Assembly.

Clutch switch input shaft, outside roll of the hull with the exception of the gearbox clutch switch between gears of the output shaft and the planetary mechanism (PM), and tubular shafts in this area, the imposition of gear rims and drove corps epicycle wheel to the periphery, a connection in one slide the boom clutch switch three States PM simplify the design, reduce the size and intensity of the transmission Assembly.

Figure 1 shows the kinematic diagram of the 16-speed non-axial Volynoblenergo transmission. In the lower part of figures 1, 2, 3 and 4 indicated a pair of external gears of the gearing.

Figure 2 presents the radial chart KP tables 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 is constant for each 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. Clutch D provides three States of the planetary mechanism (PM): I - Uhab=- ; II - Ubah=To+1; III - U(bh)=1.0, where K - internal the parameter PM 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 bearings of the housing CP 1 (see figure 1) coaxially mounted input shaft 2 and the input shaft 3. Parallel coaxial shafts 2 and 3 posted by the output shaft 4, the shaft drove 5 and the output shaft 6. On the primary shaft 3 is fixed to the gear 7, on the one hand freely mounted gear 8, and on the other hand - block of the two gears 9 and 10. On the secondary shaft 4 freely installed the unit of gears 11 and 12, meshed with gears 8 and 7 of the primary shaft, and the gears 13 and 14, the engagement with the gear train 9 and 10 on the primary shaft. The output of the output shaft 4 is fixed sun gear 15 (a) PM, which is geared with satellites 16, located on the axes of the carrier 17 (h), satellites 16 meshed with epicycle wheel 18 (b). Gear 8 of the tubular shaft 19 is connected with a ring gear 20, next to him on the primary shaft 3 fixed crown gear 21, and the input shaft 2 is fixed, three-speed gear 22, it is a three-position clutch switch 23 (a). Dip dual clutch comprises two clutch: clutch 24 is settled and the ring gear of the pinion shaft 7 3, and the opposite of the expanded sleeve 25 is on the toothed crown gear 13 of the output shaft 4, the clutch interconnected with a fork switch 26. Dip the clutch 27 (C) is located on the hub of the output shaft 4 between the gears 13 and 14. Crown gear 28 fixed on the tubular shaft 29 of the housing epicycle wheel 18, next to it on the shaft drove 5 fixed-position crown gear 30. On the output shaft 6 fixed three-position crown gear 31, which is the clutch switch 32 with three inner teeth, the crowns, which is movably connected to the slider 33. The slider 33 is fixed ring gear 34 with internal and external links, external gearing interconnected with three-position ring gear 35 of the housing 1, opposite him are crown gear 36 led 17 and the ring gear 37 of the housing epicycle wheel 18.

Pets another location coupling: coupling 24 on the toothed crown gear 9, and the sleeve 25 on the toothed crown gear 12. Instead of coupling And (23) it is possible to install a friction clutch switch.

Work, such as : a non-axial Volynoblenergo transmission is as follows:

Neutral condition (KP off) is provided at the middle position of the clutch 23 (a), when the right crown clutch is located between the gear rims 20 and 21.

16-I transfer

ufty a and C 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 a ring gear 22, a sleeve 23 (a) is transmitted to a ring gear 21, the primary shaft 3, the clutch 24, a pair of gears 9-13 (3 pair), and the sleeve 25 in this position separates the gears 12 and 13, further coupling 27 (C) on the output shaft 4 and the sun gear 15. The slider 33 outputs the ring gear 34 of the connection with the toothed crowns 36 and 37, none of the links in PM is stopped relative to the housing 1. The clutch 32 connects the ring gear 28 of the housing epicycle wheel 18 with a ring gear 30 of the carrier 17 (see figure 1, bottom right), the planetary mechanism is locked and all three of his team rotate at the same speed. The clutch 32 connects the sprockets 28 and 30 with a ring gear 31 of the output shaft 6. The output shaft 6 rotates at a speed greater than the speed of the input shaft 2.

Radiation diagram this transmission is represented by two beams: beam 3 from t on the lower horizontal left (see figure 2) up to the left to the middle horizontally and then vertically upward beam U(bh)=1,0 to t.16..

15-I transfer

Switchable coupling In the left position. Instead of a pair of gears 9-13, the work included a pair of gears 7-12.

To the shaft 3 the torque is transmitted as in the previous transmission, then a pair of gears 7-12 (2 pair), the clutch 25 to the gear 13, and then as PR is ditusa transfer.

Radiation diagram this transfer is depicted by rays 2 from t right up and then the beam U(bh)=1,0 vertically upwards to t.15.

14-I transfer

Return the clutch in the right position, the clutch And switched also in the right position.

Torque from the input shaft 2 is transmitted to a ring gear 22, a sleeve 23 (a), a ring gear 20, the tubular shaft 19 by a pair of gears 8-11 (1 pair), then the pair of gears 12-7 (2 pair) in the accelerating mode, the clutch 24, a further pair of gears 9-13 (3 pair) in the accelerating mode, the clutch 27 (C) on the output shaft 4, then as in the previous transmission.

Radiation diagram of this transfer owns four beam: beam 1 from t right up, then beam 2 down the left, then the beam 3 up and left vertical beam U(bh)=1,0 to t.

13-I transfer

Switchable coupling In the left position. In the work of only a pair of gears 8-11 (1 pair).

To the gear 11 and the torque is transmitted on the 14-th transmission, on the sleeve 25 to the gear 13, the clutch (27) on the output shaft 4, then as in the previous transmission.

Radiation diagram of the beam 1 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 by switching the clutch from the left position to the right.

12-I transfer

Switchable clutch In and in the right position, and the clutch And left. Instead of a pair of gears 8-11, the work included a pair of gears 10-14 (4 pair).

Torque from the input shaft 2 clutch (A) 23 is transmitted to the ring gear 21, the primary shaft 3 to the pinion gear 7, the clutch 24 to the gear train, the pair of gears 10-14 on the output shaft 4, then as in the previous transmission.

Radiation diagram of the beam 4 from t right up and vertical beam to vol.12 characterize this transfer.

11-I transfer

Switchable coupling In the left position. To a pair of gears 10-14 in the operation further includes a pair of gears 7-12 and 13-9.

To gear 7 torque is transmitted as in the previous transmission, then a pair of gears 7-12, the clutch 25, a pair of gears 13-9 then as on a previous pass.

Radiation diagram of this transfer owns four beam: beam 2 from t right up, then the beam 3 to the right, down, then the beam 4 to the right up and vertical beam to t.

10-I transfer

Switchable couplings a and b in the right position - turn off from work a couple of gears 9-13 and include a couple of gears 8-11 (1 pair).

Up clutch 24 and the gear 9 and the torque is transmitted on the 14-th transmission, then a pair of gears 10-14, the clutch (27) on the output shaft 4, then as in the previous transmission.

Radiation diagram of this transfer owns four beam: beam 1 from t right up, then beam 2 down the left, then the beam 4 to the right up and vertical beam to V.10./p>

9-I transfer

Switchable coupling In the left position is off from work a couple of gears 12-7 and include a couple of gears 13-9 (3 pair).

To the gear 11 and the torque is transmitted as in the previous transmission, then the clutch 25, a pair of gears 13-9, then as in the previous transmission.

Radiation diagram of this transfer owns four beam: beam 1 from t right up, then the beam 3 to the right, down, then the beam 4 to the 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 and works in the mode of the gearbox with a transmission ratio Ubah=K+1 (see figure 1 top right). Ring gear 34 connects the ring gear 35 of the housing 1 with a ring gear 37 epicycle wheel 18 and stops it relative to the housing 1. Torque acts on the sun gear 15 and is removed from carrier 17 of the shaft 5. For example:

8-I transfer

Coupling a and C are in the left position, the clutch is on the right, the clutch D is in position II (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 to a ring gear 21, the primary shaft 3, the clutch 24, a pair of gears 9 to 13, further coupling 27 (C) on the output shaft 4 (the sleeve 25 in this position separates the gears 12 and 13), solar sixth is Erny 15. The sun gear 15 rotates the satellites 16, which objetivas relatively stopped epicycle wheel 18, rotate pinion carrier 17 with slow speed. The clutch 32 connects the ring gear 3 shaft drove 5 with a ring gear 31 of the output shaft 6. The output shaft 6 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 beams: beam 3 from t on the lower horizontal left (see figure 2) up to the left to the middle horizontal line and then the beam Ubah=K+1 right up to 8.

1st gear

Switchable couplings a and C in the right position, and the clutch is to the left.

To the sun gear 15 of 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 1 from t right up, then the beam 3 to the right, down, then the beam 4 to the right up and gently sloping beam Ubah=K+1 right up to vol.1

Reverse gear is different from the previous transmission only switching clutch D from position II to position I. the ring Gear 34 of the slide 33 connects the ring gear 35 with the ring gear 36 and drove stops drove 17 relative to the housing 1. Torque acts on the sun gear 15 and is removed from epicycle wheel 18, the planetary mechanism is the mode of the gearbox with a transmission ratio U hab=-K, the output shaft 6 rotates in the direction opposite to the rotation of the sun gear 15. For example:

1st reverse gear

Coupling a and C are in the right position, the clutch is in the left, the clutch D is in position I.

Torque (see figure 1) from the input shaft 2 to the sun gear 15 is passed as the 1st and 9th the forward stroke. The sun gear 15 rotates the satellites 16, which objetivas relative to the stopped carrier 17, rotate epicycle wheel 18 in the direction opposite to the rotation of the sun gear 15. On the tubular shaft 29 through the gear 28, the clutch 32 torque enters the ring gear 31 of the output shaft 6.

Radiation diagram of this transfer owns four beam: beam 1 from t right up, then the beam 3 to the right, down, then the beam 4 to the right up and gently sloping beam Uhab=-Left down to .1R.

8-I reverse gear

Coupling a and C are in the left position, the clutch is on the right, the clutch D is in the first position.

Torque (see figure 1) from the input shaft 2 is transmitted to the output shaft 4 and the sun gear 15 on the 8th and 16th the speeds forward, hereinafter referred to as a previous pass.

Radiation diagram this transmission is represented by two beams: beam 3 from t on the lower horizontal left (see figure 2) left up to the average horizontal and daneelec U habhollow right down to .8R.

Such as : a non-axial valvoplasty transmission, comprising a housing placed in parallel the primary and secondary shafts, arranged them in four rows of pairs of meshed gears, two gears on each shaft are combined in blocks, 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 mounted on the toothed crown gear secondary shaft, the hub of the output shaft between the loosely mounted gear is the clutch switch, the output of the secondary shaft fixed sun gear of the simple three planetary gear, carrier and housing epicycle wheels are sprockets located next to the ring gear housing, gear output shaft position, characterized in that the input shaft with the ring gear and installed the clutch switch is located coaxially with the primary shaft, which is fixed to gear, next to it is checked gear tubular shaft, which is fixed to the gear, meshed with the gear block is and gear secondary shaft, the second gear unit meshed with the gear fixed on the primary shaft, gear shaft drove off, clutch switch, mounted on the ring gear of the output shaft has three internal gear on the slide that the clutch switch is rigidly fixed ring gear with internal and external links, external toothing of which is connected with the three-position ring gear housing Assembly.



 

Same patents:

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2 dwg

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2 dwg

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2 dwg

Gear box // 2253781

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Gear box // 2254507

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises housing (1) made of the front and rear cap-shaped parts whose longitudinal walls are mating in the transverse plane. The housing receives input shaft (16) with pinion (22), side shaft (17) with pinions (23)-(25), intermediate shaft (19), output shaft (18), and three-link planet mechanism (37) with the device for its locking and connecting its link with the reactive gear member (38) connected with housing (1). Shafts (16)-(19) with pinions and planet mechanism (37) are arranged in the single space between front (5) and rear (10) outer walls of housing (1) which define supports for the shafts.

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4 cl, 4 dwg

FIELD: mechanical engineering.

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24 cl, 1 tbl, 10 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: proposed gearbox contains input shaft 2 and output shaft 4 arranged in parallel. Four gears 9, 11, 12, 19 are united to form cluster by shaft 3. Gears 16-18 of output shaft 4 are in pair meshing with gears 9-12 of cluster. Gear 19 of cluster engages with gear 22 of output shaft through idler gear or cluster of two reverse gears 21-21. Two shifter sleeves 32, 33 are installed on hubs of output shaft 4. Input shaft 2 is arranged coaxially to four gear cluster shaft. One of gears 6 of input shaft is fixed, and gears 7, 8 are freely fitted. Said three gears are in pair meshing with gears 13-15 freely fitted on output shaft 4. Three two-position twin shifter sleeves A, B, C are installed between four pairs of gears being arranged on gears of parallel shafts. One member is installed on rim of gear of input shaft 2, other member is installed opposite to first member on rim of gear of output shaft 4. Members are intercoupled by three shifter forks 25, 28, 31. Invention provides up to 24 forwards speeds and up to 8 reverse speeds.

EFFECT: enlarged operating capabilities of vehicle.

1 tbl, 2 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: proposed gearbox has housing 1, input shaft 2 and output shaft 5 arranged parallel to each other, four gears 9, 11, 12, 17 united into cluster by shaft 3 arranged coaxially with input shaft 2, tubular shaft 20 with gears 12 and 13 freely fitted on output shaft 5 and gears 14, 15, 19 in meshing with cluster gears. Three-position sleeve A installed on input shaft 2 between first and second rows of gears. Three-position shifter sleeves C, D are installed on hubs of out[put shaft 5 between pairs of low gears and row of reverse gears. Gear 8 is freely fitted on input shaft 2 between hub of three-position shifter sleeve A and shaft 3 of gear cluster, said gear being in meshing with gear 13 of tubular shaft 20. Gear 14 which is in meshing with cluster gear 9 is freely fitted near gear 13 on outer shaft 5. Two position twin shifter sleeve B is arranged between second and third rows of gears. Said shifter sleeve consists of two-position members 22 and 23. Member 22 is installed on rim of gear 8 of input shaft 2. Member 23 is installed opposite to first member on rim of gear 14 of output shaft 5. Members are intercoupled by shifter fork 24. Invention provides up to 12 forwards speeds and up to reverse speeds.

EFFECT: enlarged operating capabilities of vehicle owing to increased number of forward and reverse speeds.

1 tbl, 2 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: proposed gearbox has housing 1, drive shaft 2, main shaft 3 and countershaft 4. Drive shaft 2 and main shaft 3 are installed coaxially. Countershaft 4 is arranged in parallel with shafts 2 and 3. Gears 9-12 of countershaft 4 are engaged in pairs with gears 15-18 freely fitted on main shaft 3. Low-speed gears 10-12 and reverse gear 19 are secured on countershaft 4. Reverse idler gear 20 s arranged on axle 5 between countershaft 4 and main shaft 3. Tubular shaft 13 with gears 7 and 8 is installed on countershaft 4. Gears 7 and are in meshing with gears 6, 14 freely fitted on drive shaft 2 and main shaft 3. Hub of three position shifter sleeve A is secured on drive shaft 2. Three-position shifter sleeves D, E are arranged on hubs main shaft 3 at gearbox outlet between row of reverse gears and three pairs of low-speed gears. Two two-position twin shifter sleeves B and C, each consisting of two-position members, are placed between second, third and fourth rows of gears. Said members are fitted on gears of adjacent rows of parallel shafts and are interconnected by shifter forks 27, 30. Invention provides up to 24 forwards speeds and up to 8 reverse speeds.

EFFECT: enlarged operating capabilities of vehicle owing to increased number of forwards and reverse speeds.

1 tbl, 2 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet mechanism comprises solar pinion (43), carrier (41) with satellites (42), gear wheel (39) with synchronizers (54) and (55), and ring spring pusher (61) of the synchronizer that cooperates with teeth (48) of wheel (39). Pusher (61) is interposed between satellites (42) and synchronizer (54). Teeth (48) of wheel (39) in the zone of cooperation with pusher (61) are provided with transverse grooves (62-64).

EFFECT: reduced axial size.

6 cl, 10 dwg

FIELD: transport engineering.

SUBSTANCE: proposed multi-speed gearbox has housing 1, input shaft 2 and output shaft 4 arranged in parallel. Gear 6 is fixed, and gears 7 and 8 are installed for sliding on input shaft 2. gears 9, 11, 12, 19 are combined into cluster by shaft 3. Gears 6-12 are engaging in pairs with gears 13-18 freely fitted on output shaft 4. Three two-position twin shifter sleeves A, B and C are installed between four pairs of gears 6-13, 7-14, 8-15 and 9-16. Each shifter sleeve consists of two-position members located on gears of adjacent rows of parallel shafts intercoupled by shifter for. Member 23 is installed on rim of hear 7 of input shaft 2, and member 24 is installed opposite to first member on rim of gear 13 of output shaft 4. Two shifter sleeves D and C are installed on hubs of output shaft 4 between two pairs of low gears and reverse gear.

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

1 tbl, 2 dwg

Gear box // 2267675

FIELD: mechanical engineering.

SUBSTANCE: gear box comprises housing (1), shafts (16), (17), (18), and (19) with pinions, and three-sprocket planet mechanism (37) provided with a device for its locking. Crown wheel (39) of the planet mechanism is connected with the reaction gearing member (38) mounted on the inner surface of back outer wall (10) of the housing.

EFFECT: reduced sizes.

5 cl, 4 dwg

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