RU2295457C1 - Multistep coaxial shaft-and-two planetary train transmission - Google Patents

Abstract

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.

2 dwg

Description

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

Known transmission units with a step change in gear ratios, containing gears, shafts, bearings, gear shifting devices used in domestic and foreign cars. (Automobiles: Design, construction and calculation. Transmission. / Ed. By A.I. Grishkevich. Mn .: Vysh. Shk., 1985. - 240 p.).

These units are structurally complex, metal-intensive.

Closest to the proposed multi-stage all-twin planetary gearbox (MKP) is KP according to patent RU 2217325 C1 (Bull. No. 33 of 11/27/2003).

The gearbox contains an aggregate housing in which a three-shaft coaxial gearbox with three pairs of intermeshing gears of external gearing is located, gears on the primary and secondary shafts of the gearbox are installed freely, two gearshift clutches are located between them, gears on the intermediate shaft are combined into a block, located at the output of the aggregate simple three-link planetary mechanism with a carrier, satellites, an epicyclic wheel and a sun gear fixed on a secondary shaft, primary, secondary reduction shafts the torus, the output shaft of the carrier and the output shaft of the unit are coaxial, the casing of the three-shaft gearbox, the tubular shaft of the carrier and the body of the epicyclic wheel have adjacent toothed crowns, the body of the epicyclic wheel on the other hand, the output shaft of the carrier and the output shaft of the unit have adjacent gear crowns, on a gear clutch is installed on the gear tooth of the output shaft of the unit, which has two internal gear gears, it is shifted with a switching fork and a slider interconnected with a gear clutch having VA internal gears mounted on the gears of the gear housing.

The described gearbox is simpler than the typical designs of transmission units described in the book, but has limited operational capabilities when used on heavy vehicles with high-torque engines, since it does not provide a sufficient range of gear ratios (the ratio of gear ratios of lower gear to higher), gear shifting is difficult when changing direction of movement, since between the reverse and lower gear subbands the higher gear subband is located, the design is complicated Due to the increased size of the gear freely mounted on the input shaft, the gear ratio in gearing is limited due to the switching clutch stopping the carrier or the epicyclic wheel relative to the gear case.

The problem to which the invention is directed is to expand the operational capabilities of the vehicle due to the possibility of transforming large torques, expanding the range of gear ratios and increasing the number of gears, optimizing gear shifting while simplifying the design and reducing the metal consumption of the components of the transmission unit.

The problem is solved by achieving a technical result, which consists in using an additional planetary mechanism (PM), increasing the number of gears and increasing the range of gear ratios of both the shaft gearbox and the unit as a whole, while reducing the size and metal consumption of its components, improving the switching mechanism gears of the main planetary gear.

The specified technical result is achieved in that the multi-stage coaxial shaft-two-planet gearbox contains an assembly body in which a three-shaft coaxial gearbox with three pairs of intermeshing gears of external gearing are located, two gears on the intermediate shaft are combined into a block, gears on the gearbox secondary shaft are mounted freely, between them is located gear shift clutch, at the output of the unit there is a basic simple three-link planetary gear with a carrier, satellites, solar the gear wheel and the epicyclic wheel, the primary and secondary gear shafts, the carrier output shaft and the output shaft of the unit are aligned, the carrier and the epicyclic casing have adjacent gears, the tubular shaft of the epicyclic wheel housing, the carrier output shaft and the output shaft of the gear have adjacent gear crowns , a switching clutch is installed on the gear rim of the output shaft of the unit, which is interconnected with a slide with a switching fork, the gear on the input shaft is fixed, it is engaged In conjunction with a gear having a gear ring of increased width freely mounted on the countershaft, the gear of the secondary shaft also has a gear ring of increased width next to the gear ring of the gear of the input shaft, there is a gearshift clutch on these gear crowns, interconnected by a shift fork with another coupling half installed on the gear rims of the gears of the intermediate shaft, the gear rim of the output shaft of the carrier is on-off, the gear rim of the output shaft of the unit is three-position, the clutch This crown has three internal ring gears, on the slide of the switching clutch there is a ring gear with internal and external gearing, the external gearing of which is connected with the three-position gear ring of the unit body, between the coaxial shaft gear and the main three-link planetary gear an additional three-link planetary gear is installed, he has a sun gear fixed to the output of the secondary shaft, a ring gear and a sun gear of the main plan are fixed on the output shaft of the carrier ary mechanism toothing tubular shaft epicyclic gear wheel located between the rims of the output shaft carrier housing and septum assembly, these toothings arranged switching sleeve.

An additional three-link planetary mechanism doubles the number of gears and allows you to significantly increase the range of the manual gearbox, as it has a high bearing capacity (can transform large torques); the gear, freely mounted on the input shaft, had an increased diameter, it limited the range of gear ratios of the shaft reducer, increased its dimensions and metal consumption due to an increase in the center distance. The planetary gear mechanism (PM) of the prototype gearbox provided three modes of operation, but not in the optimal mode, when changing from a lower gear to a reverse gear, one must go through the position of the higher gears; to change gears, two couplings with a movable connection between them were required.

The proposed technical solution allows to increase the transmitted torque, gear ratio range and double the number of gears due to an additional three-link planetary gear with gears on the carrier’s output shaft, epicyclic wheel tubular shaft and the unit’s baffle with switching clutch, and to reduce the size and metal consumption of the shaft reducer due to combining the gears with the input shaft, simplify the gearshift mechanism through the use of gears with internal and external gears instead of switching the clutch captivity and implement three modes PM with optimum gearshift mode: IU ^h _ab = -K; II-U ^b _ah = K + 1; III-U _(bh) = 1 when installing a two-position gear ring of the output shaft of the carrier and a three-position gear ring of the output shaft of the unit.

In Fig.1 shows a diagram of the MCP, in Fig.2 is a beam diagram and tables of the position of the clutch on different gears forward (top) and reverse (bottom).

The vertical beam corresponds to a gear ratio of one. The greater the slope of the beam, the higher the gear ratio. On a logarithmic scale, the beam tilt is constant on any part of the radiation pattern. Rays of pairs of gears of external gearing are designated I, II, III; and the rays characterizing the modes of operation of planetary mechanisms - U = 1,0; U ^b _ah and U ^h _ab .

In the bearings of the unit body 1, the primary shaft 2, the secondary shaft 3, the output shaft of the additional PM 4 carrier, the output shaft of the main PM 5 carrier and the output shaft of the unit 6 are coaxially aligned. In parallel, the intermediate shaft 7 is mounted on which the gear 8 is freely mounted and the block is fixed gears of external gearing 9 and 10. These gears are interconnected with gears of external gearing 11, 12 and 13, gear 11 is mounted on the primary shaft 2 (made integral with it), gears 12 and 13 are freely mounted on the secondary shaft 3. On the secondary the sun gear 14 of the additional PM is fixed to the shaft 3, which is engaged with the satellites 15 mounted on the axles of the carrier 16 and engaged with the epicyclic wheel 17. The tube of the epicyclic wheel 17 is connected to the ring gear 19 by the tubular shaft 18. On the output shaft, it drove 4 next to the ring gear 19 fixed ring gear 20 and sun gear 21 of the main PM. A gear ring 22 is fixed on the partition wall of the unit body 1 next to the ring gear 19, and a switch clutch 23 (C) is mounted on these ring gears. The sun gear 21 of the main PM is engaged with the satellites 24 mounted on the axles of the carrier 25 and engaged with the epicyclic wheel 26. The tube of the epicyclic wheel 26 is connected to the one-position gear ring 28 by the tubular shaft 27. On the output shaft of the carrier 5 of the main planetary gear next to the gear ring 28 is fixed a two-position gear ring 29. A three-position gear ring 30 is fixed on the output shaft of the unit 6 next to the gear rims 28 and 29. A gear wheel is located on the outer surface of the epicyclic wheel case 26 crown 31. Next to the ring gear 31 is the ring gear 32 of the carrier 25. The three-position ring gear 33 is mounted on the unit body 1 opposite the ring gears 31 and 32. The shift clutch (A) consists of two coupling halves 34 and 35 connected by a shift fork 36, they mounted respectively between gears 11-12 and 8-9. The clutch 37 (B) is installed on the hub of the secondary shaft 3 between the gears 12 and 13. The clutch (D) 38 is located on the gear ring 30 of the output shaft of the unit 6. The shifting fork 39 is slidably connected to the shifting clutch 38 by the slider 40, fixed to the inner end of the slider 40 ring gear 41 with internal and external gears.

The work of the CP is as follows.

First gear

The coupling half 34 and the shift clutch (B) 37 are in the right position (P) - (see Fig. 2 table at the top right), the shift clutch C (23) is in the left position (L), the shift clutch D (38) is in middle position (II). In this case (see Fig. 1) the coupling half 34 disconnects the gear 12 from the input shaft 2, the coupling half 35 connects the gear 8 to the gear 9 of the intermediate shaft 7, the coupling B (37) connects the gear 13 to the secondary shaft 3. Coupling C (23) connects the ring gear 19 of the tubular shaft 18 of the epicyclic wheel 17 of the additional PM with the gear ring 22 of the partition wall of the unit body 1, the additional PM is in the mode with the gear ratio U ^b _ah = K ₁ +1. The gear ring 41 connects the gear rims 33 of the unit body 1 and 31 of the main PM epicyclic wheel body 26, the coupling D (38) with the middle inner rim (see Fig. 1, top right) connects the gear ring 29 of the output shaft 5 to the gear ring 30 of the output shaft unit 6. The main PM is in a mode with a gear ratio U ^b _ah = K ₂ +1. The upper symbol indicates the stopped link - b, the lower symbols - the links of the input (a - sun gear) and the output (h - carrier) of torque, K - internal PM parameter, equal to the ratio of the numbers of teeth of the epicyclic wheel and the sun gear - for ray diagram of the embodiment for the additional PM - K ₁ = 1.5; for the main PM - K ₂ = 5.3.

Torque from the input shaft 2 and gear 11 is transmitted to gear 8 (pair of gears I), the coupling half 35 is transmitted to gear 9, along the intermediate shaft 7 to gear 10, then to gear 13 (pair of gears III). From the gear 13 of the clutch switch B (37), the torque is transmitted to the secondary shaft 3 and the sun gear 14 of the additional PM. The sun gear 14 rotates the satellites 15, which, rolling around a stopped epicyclic wheel 17, transmit increased torque to the carrier 16, the output shaft of the carrier 4, the sun gear 21 of the main PM. The sun gear 21 rotates the satellites 24, which, rolling around the stopped epicyclic wheel 26, transmit even more increased torque to the output shaft 5, the gear ring 29, the shift clutch D (38), the gear ring 30 and the output shaft of the unit 6.

In the beam diagram, this transmission corresponds to four series-connected beams: from t.0 on the second from the bottom left of the scale (see figure 2), beam I is right down, then beam III is right up, and then gentle beams U ^b _ah to t.1 from right to top scale.

Second gear

We move the coupling A to the left position - the coupling half 34 connects the gears 11 and 12, the coupling half 35 disconnects the gears 8 and 9, while the pairs of gears II and III are included in the operation.

The torque from the input shaft 2 is transmitted by the coupling half 34 to the gear 12, then to the gear 9 (a pair of gears II), from the intermediate shaft 7 to the gear 10, from it to the gear 13 (a pair of gears III), via the coupling 37 to the secondary shaft 3, then as in the previous gear.

Four rays correspond to this transmission in the radiation diagram: II — to the right down, III — to the right up, and two beams U ^b _ah — also to the right up to the point 2.

Third gear

We switch the clutch A from the left position to the right, and the clutch B - to the left - the coupling half 34 disconnects the gear 11 from the gear 12, the coupling B (37) connects the gear 12 to the secondary shaft 3, and gear pairs I and II are included in the operation.

From the primary shaft 2, the torque is transmitted to a pair of gears 11-8, then through the coupling half 35, gears 9-12 and clutch B to the secondary shaft 3, then as in previous gears.

On the ray diagram of this transmission, the rays I, II and U ^b _ah correspond, directed from t.0 to t.3.

Fourth gear

We move clutch A to the left position - we obtain direct transmission in the shaft gearbox.

The torque from the input shaft 2 is transmitted by the coupling half 34 to the gear 12, the coupling 37 to the secondary shaft 3, then as in previous gears.

On the beam diagram, this transmission corresponds to two beams U ^b _ah directed from v. 0 to v. 4.

Fifth gear

We switch couplings A, B and C from the left position to the right. Clutches A and B return the shaft gear to the first gear position. The clutch C (23) disengages from the gear ring 22 of the partition wall of the unit body 1 and connects the gear ring 19 of the tubular shaft 18 of the epicyclic wheel 17 to the gear ring 20 of the output shaft 4 of the carrier 16, while the additional PM is blocked.

Torque from the input shaft 2 by clutch A is transmitted to a pair of gears I, through an intermediate shaft 7, a pair of gears 10-13 and a clutch 37 to a secondary shaft 3, via a blocked additional PM to the sun gear 21 of the main PM and then as in previous gears.

Four rays: I, III, U = 1,0 and U ^b _ah from t.0 to t.5 represent this transmission.

Sixth gear

We switch clutch A to the left position - we replace a pair of gears I with a pair of gears II.

Before the secondary shaft 3, the torque is transmitted as in second gear, then as in the previous gear.

Rays II, III, U = 1,0 and U ^b _ah from t.0 to t.6 correspond to this transfer.

Seventh gear

We switch clutch A to the right position, and clutch B to the left.

Torque is transmitted to the secondary shaft 3, as in third gear, then as in the previous gear.

Rays I, II, U = 1,0 and U ^b _ah correspond to this transfer.

Eighth gear.

We switch clutch A to the left position - the pairs of gears of the coaxial gearbox are turned off from work.

Torque from the input shaft 2 is transmitted directly to the secondary shaft 3, then as in previous gears.

On the beam diagram, this transmission is represented by the rays U = 1,0 and U ^b _ah from t.0 to t8.

Ninth gear

Clutches A, B and C are returned to the first gear position, and the clutch D and the ring gear 41 with the slider 40 are moved to the right position III (see figure 1, bottom right). With a fixed connection of two links of the main PM relative to each other, it is blocked - all three links rotate with the same frequency. This state of the PM in the radiation diagram is represented by vertical rays - U = 1.0.

The torque to the main PM is transmitted, as in first gear, then directly along the main PM and then with gears 28 and 29, the clutch 38 to the gear ring 30 and the output shaft of the unit 6.

On the beam diagram, this transmission is represented by four rays: the first three rays I, III and U ^b _ah correspond to the first transmission, and the fourth ray is directed vertically up to point 9.

Tenth gear

We switch clutch A to the left position - the couplings of the shaft gearbox and the additional PM are in the state of second gear.

The torque to the main PM is transmitted, as in second gear, and then - as in the previous gear.

On the radiation diagram of this transmission correspond to rays II, III, U ^b _ah and U = 1,0.

Eleventh gear

Move clutch A to the right and clutch B to the left - to the third gear position.

Torque is transmitted to the main PM

 as in third gear, then - as in the last two gears.

In the beam diagram, beam I with an inclination to the right downward, beam II to the left upward, a gentle beam U ^b _{ah to the} right upward, and the beam U = 1,0 vertically upward characterize this transmission.

Twelfth gear

Switch clutch A to the left position, the first three clutches in the left position corresponding to fourth gear.

Until the main PM, the torque is transmitted as in fourth gear, then as in previous gears.

In the beam diagram, the rays U ^b _ah and U = 1,0 represent this transmission.

Thirteenth gear

We move the three couplings to the right - in the fifth gear position. Clutch C blocks an additional PM.

Until the main PM, the torque is transmitted, as in fifth gear, then on the locked main PM, as in previous gears.

Rays I, III and two rays U = 1,0 characterize this transmission.

Fourteenth gear

Switch clutch A to the left.

Until the main PM, the torque is transmitted as in sixth gear, then as in previous gears.

Rays II, III and two rays U = 1,0 correspond to this transmission.

Fifteenth gear

Switch clutch A to the right and clutch B to the left.

Torque to the main PM is transmitted as in seventh gear, then as in previous gears.

Rays I, II and two rays U = 1,0 represent this transmission.

Sixteenth gear - direct

Move clutch A to the left.

Up to the main PM, the torque is transmitted, as in the eighth gear, then - as in the last gears.

On the beam diagram, this transmission is represented by two vertical rays U = 1,0 from t.0 to t.16.

Reverse gears are provided by the main PM when switching the ring gear 41 and clutch D to position I - while the ring gear 41 connects the ring gear 32 of the carrier 25 of the main PM to the ring gear 33 of the unit body 1 and stops the carrier, the coupling 38 connects the ring gear with the middle inner ring 28, the tubular shaft 27 of the epicyclic wheel 26 with the ring gear 30 of the output shaft 6. The main unit is operating in the PM U ^b _ah = -K _2, the sun gear 21, pinion 24, mounted on the axes a stopped carrier 25 rotates slowly epicycle cal wheel 26 and the output shaft of the unit 6 in the opposite direction.

First reverse - 1R

We install the couplings A, B and C in the position of the first gear for moving forward, and the clutch D - in position I (see figure 2 table at bottom right).

To the main PM, the torque is transmitted, as in the first forward gear, then from the sun gear 21 by satellites 24 to the epicyclic wheel 26, then along the tubular shaft 27, gear ring 28, clutch 38, gear ring 30 to the output shaft of the unit 6.

On the radiation diagram, this reverse gear is represented by four beams: I, III, U ^b _ah and U ^b _ah = -K ₂ from t.0 to t.1R.

Second Reverse - 2R

Switch clutch A to the left position.

The torque to the main PM is transmitted, as in the second forward gear, then as in the previous gear.

Four rays correspond to this transmission on the radiation diagram: II, III, U ^b _ah and U ^h _ab = -K ₂ .

Third Reverse - 3R

Switch clutch A to the right position and clutch B to the left position.

Up to the main PM, the torque comes in both the third forward gear and then the last two gears.

On the beam diagram, four rays: I, II, U ^b _ah and U ^h _ab = -K ₂ characterize this transmission.

Fourth Reverse - 4R

Move clutch A to the left position.

To the main PM, the torque is transmitted, as in the fourth forward gear, then as in the last gears.

The gentle rays U ^b _ah and U ^h _ab = -K ₂ from t. 0 to t. 4R represent this transmission.

Fifth Reverse - 5R

We move all three gearbox couplings from left to right.

Torque to the main PM is transmitted, as in fifth gear forward and further as in previous gears.

Rays I, III, U = 1,0 and U ^h _ab = -K ₂ correspond to this transmission.

Sixth Reverse - 6R

Switch clutch A to the left position.

The torque to the main PM is transmitted, as in the sixth forward gear, then as in previous gears.

Rays II, III, U = 1,0 and U ^h _ab = -K ₂ correspond to this transmission.

Seventh Reverse - 7R

Switch clutch A to the right and clutch B to the left.

To the main PM, the torque is transmitted as in the seventh forward gear, then as in the last gears.

Rays I, II, U = 1,0 and U ^h _ab = -K ₂ correspond to this transmission.

Eighth Reverse - 8R

Move clutch A to the left position.

Torque through the shaft gearbox and additional PM is transmitted directly and converted only to PM.

In the beam diagram, the rays U = 1,0 and U ^h _ab = -K ₂ correspond to this transmission.

When changing the parameters of the gears of external gearing and PM, the distribution of gears and the tilt of the rays will also change.

Claims (1)

A multistage coaxial shaft-two-planet gearbox containing an aggregate housing in which a three-shaft coaxial gearbox with three pairs of intermeshing gears of external gearing are located, two gears on the intermediate shaft are combined into a block, gears on the secondary gearbox shaft are mounted freely, between them there is a gear shift clutch, at the output of the unit there is a basic simple three-link planetary mechanism with a carrier, satellites, a sun gear and an epicyclic wheel, primary, second Reducer shafts, carrier output shaft and aggregate output shaft are aligned, the carrier and the epicyclic casing have adjacent gears, the tubular shaft of the epicyclic wheel housing, the carrier output shaft and the output shaft of the gear have adjacent gears on the gear of the output shaft of the unit a shift clutch is installed, which is interconnected with a slide with a shift fork, characterized in that the gear on the input shaft is fixed, it is engaged with the gear having a tooth a crown of increased width freely mounted on the intermediate shaft, the gear of the secondary shaft also has a gear ring of increased width next to the gear ring of the gear of the input shaft, on these gear crowns there is a gear coupling half interconnected by a shift fork with another coupling half mounted on the gear crowns of the gears of the intermediate the shaft, the gear ring of the output shaft of the carrier is on-off, the gear ring of the output shaft of the unit is on-off, the shift clutch on this crown has three internal gear rings, on the slide of the switching clutch, a gear ring with internal and external gearing is rigidly fixed, the external gearing of which is connected with a three-position gear ring of the unit body, an additional three-link planetary mechanism is installed between the coaxial shaft gear and the main three-link planetary gear, its sun gear is fixed on the output of the secondary shaft, on the output shaft of the carrier, a gear ring and a sun gear of the main planetary mechanism are fixed, gear the crown of the tubular shaft of the epicyclic wheel is located between the gears of the output shaft of the carrier and the partitions of the unit body; a gear clutch is located on these gears.

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