RU2217325C1 - Gearbox - Google Patents

Abstract

FIELD: transport engineering. SUBSTANCE: invention relates to automobiles, tractors, road-building machines, mounted equipment drives of special vehicles, etc. Proposed gearbox contains three-shaft reduction unit with coaxial primary and secondary shafts, countershaft parallel to said shafts and two shifter sleeves, three-member planetary mechanism, set output shaft coaxial with planetary mechanism and two intercoupled sleeves one of which is installed on set housing, and the other on set output shaft. Two invercoupled shifter sleeves provide operation of planetary mechanism in three modes: direct drive, maximum gear ratio with epicyclic wheel stopped, and reverse rotation of output shaft with carrier stopped. Performance characteristics of vehicle are improved owing to increased number of forward speeds up to eight and reverse speeds up to four at increased efficiency owing to preventing operation of planetary mechanism at summing mode. EFFECT: improved service capabilities. 2 dwg

Description

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

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

 These units are structurally complex, metal-intensive.

 Closest to the proposed gearbox (KP) is KP according to patent RU 2053135 (Bull. N 3 from 01/27/1996).

 The gearbox contains a housing of the unit 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, at the output of this gearbox there is a simple three-link planetary mechanism with a carrier, satellites, a sun gear and an epicyclic wheel, primary, secondary gear shafts, a carrier output shaft and the output shaft of the unit are coaxial, the body of the epicyclic wheel, the output shaft of the carrier and the output shaft of the unit have adjacent gear rims, a gear clutch is installed on the gear rim of the output shaft of the aggregate.

 The described gearbox is simpler than the typical designs of transmission units described in the book, provides a sufficient range of gear ratios (the ratio of gear ratios of lower gear to higher), but has limited operational capabilities at low speeds due to the large interval between first and second gears, as well as reduction the efficiency of the unit during operation of the planetary gear in the summing mode, especially with significant gear ratios (first gear and reverse).

 The problem to which the invention is directed, is to expand the operational capabilities of the vehicle.

 The problem is solved by achieving a technical result, which consists in increasing the number of gears of both forward gear from six to eight and reverse gear from one gear to four, uniform distribution of gears over the range, elimination of the planetary gear operation in the summing mode with low efficiency.

 The specified technical result is achieved by the fact that the gearbox containing the housing of the unit, in which there are a three-shaft coaxial gearbox with three pairs of interlocked gears of external gearing, the gears on the primary and secondary shafts of the coaxial gearbox are installed freely, between them there are two gearshift clutches, gears on the intermediate the shaft is combined into a block, at the output of this coaxial gearbox there is a simple three-link planetary mechanism with a carrier, satellites, a sun gear and epic by the cliched wheel, the primary, secondary gear shafts, the carrier output shaft and the output shaft of the unit are aligned, the epicyclic wheel body, the carrier output shaft and the output shaft of the gear have adjacent gear crowns, a shift clutch is installed on the gear crown of the output shaft of the aggregate, the sun gear of the planetary gear mounted on the secondary shaft of the gearbox, the body of the epicyclic wheel and the tubular drive shaft of the carrier have adjacent gear rings located next to them on the inner wall of the housing a gear ring is located on the unit, on which a switching clutch is installed, interconnected by a slider with a switching clutch of the output shaft of the unit, the inner ring of which has an increased width.

The planetary gear mechanism (PM) of the prototype gearbox provided two operating modes: one in which the torque was applied to two links: the sun gear and the carrier, and removed from the third link - the epicyclic wheel, and the second, in which the two PM links are closed together, PM is blocked and works with a gear ratio U _(bh) = 1. The number of gears of the unit is equal to twice the number of gears of the coaxial gear minus one - seven gears: six forward gears and one reverse gear. The distribution of gears over the range is not optimal - the interval between gears increases in the lower gear zone, with large gear ratios, the efficiency of the unit decreases sharply. There is a variant of selection of rotation speeds of the leading links, at which the output link will be fixed, i.e. the efficiency of the unit in this case is zero.

The proposed technical solution allows you to implement three modes of operation of the PM: U _ah ^b = K + 1; U _(bh) = 1; U _ab ^h = -K. The number of gears of the unit is equal to three times the number of gears of the coaxial gearbox - twelve gears: eight forward gears and four reverse gears. The distribution of gears over the range is optimal - equal intervals between gears are provided, gears in the summing mode of operation of PM with low efficiency are excluded.

 In FIG. 1 shows a diagram of the gearbox; figure 2 is a beam diagram and table of the position of the clutch at different gears forward (top) and reverse (bottom).

Two scales are plotted on the middle axis of the radiation diagram: at the top is the uniform scale of the logarithm of the gear ratios, and at the bottom is the uneven scale of the gear ratios. 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 tilt of the beam 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 the planetary mechanism, -U = 1,0; U _ah ^b and U _ab ^h .

 In the bearings of the housing unit 1 coaxially located primary shaft 2, secondary shaft 3, the output shaft of the carrier 4 and the output shaft of the unit 5. In parallel, it has an axis 6 on which the gear block of the external gearing 7, 8 and 9 of the intermediate shaft is located. These gears are interlocked respectively with external gears 10, 11 and 12, freely mounted on the primary 2 and secondary 3 shafts. A sun gear 13 is fixed on the secondary shaft 3, which is engaged with the satellites 14 mounted on the axles of the carrier 15 and engaged with the epicyclic wheel 16. With the tubular shaft 17, the body of the epicyclic wheel 16 is connected to the ring gear 18. On the output shaft, it drove 4 next to the ring gear 18 a gear ring 19 is fixed. A gear ring 20 is fixed on the output shaft of the unit 5 next to the gear rims 18 and 19. A gear ring 21 is located on the gearbox housing 16 from the gearbox side 21. On the tubular shaft 22 of the drive carrier 15, next to the gear m crown 21 is a ring gear 23. The ring gear 24 is fixed on the inner wall of the housing unit 1 near the ring gears 23 and 21. The switching clutches 25 (A) and 26 (B) are mounted respectively between the gears 10-11 and 11-12. The clutch 27 (C) is located on the ring gear 24. The clutch switch 28 (D), the inner ring of which has an increased width, is mounted on the ring gear 20 of the output shaft 5. The slider 29 is movably connected to the clutch switches 27 and 28.

 Instead of the axis 6, used with a small center distance to the shafts 2 and 3, it is possible to install an intermediate shaft with gears 7-9 mounted on it.

 The work of the CP is as follows.

First gear
Switch clutch A (25) is in the left position (L) - (see figure 2 - table above, on the right), switch clutch B (26) is in the right position (P), switch clutch C and D (27 and 28 ) - in the right position (III). In this case, clutch A connects the gear 10 to the input shaft 2, clutch B - the gear 12 to the secondary shaft 3, clutch C stops the epicyclic wheel 16 (b) relative to the unit body 1, and clutch D connects the gear ring 19 of the output shaft 4 to the gear crown 20 of the output shaft of the unit 5. The planetary mechanism (PM) is in the mode with a gear ratio U _ah ^b = K + 1. The upper symbol indicates the stopped link - b, the lower symbols - the links of the input (a - sun gear) and output ( h - carrier) of torque, K - PM internal parameter equal to wearing numbers of ring gear teeth and a sun gear - for the embodiment illustrated in the diagram of radiation execution PM it is 3, and the gear ratio GR is equal to 4.

 Torque from the input shaft 2 by clutch A is transmitted to gear 10, from it to gear 7 (pair of gears I), then along the tubular shaft of the block to gear 9 and from it to gear 12 (pair of gears III). From the gear 12 of the clutch B (26), the torque is transmitted to the secondary shaft 3 and the sun gear 13. The sun gear 13 rotates the satellites 14, which, rolling around the stopped epicyclic wheel 16, transmit the increased torque to the carrier 15, the output shaft of the carrier 4, ring gear 19, shift clutch D (28), ring gear 20 and output shaft 5.

 On the beam diagram, this transmission corresponds to three series-connected beams: from t. 0 on the middle scale on the left (see Fig. 2), beam I is downward to the right, then ray III is upward to the right and then a gentle beam to t.1 to the right on the upper scale.

Second gear
We move clutch A to the right position, while the pair of gears I is turned off and the pair of gears II is turned on.

 The torque from the input shaft 2 is transmitted by the clutch A to the gear 11, then to the gear 8, then - as in the previous gear.

 Three rays also correspond to this transmission in the radiation diagram, but instead of ray I, vertical ray II is represented.

Third gear
We switch clutches A and B from the right to the left - clutch A returns to the position corresponding to the first gear, and clutch B connects gear 11 to the secondary shaft.

 Before the gear block, the torque is transmitted as in first gear, then by a pair of gears II (8-11) to the secondary shaft 3, then - as in previous gears.

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

Fourth gear
Move clutch A to the right position - both couplings are connected to gear 11.

 Torque from the input shaft 2 is transmitted to the secondary shaft 3 directly via clutches A, B and gear 11, then - as in previous gears.

On the beam diagram this transmission corresponds to one ray U _ah ^b directed from t.0 to t.4.

Fifth gear
We return the couplings A and B to the state corresponding to the first gear, and the couplings C and D are moved to position II. Clutch C leaves the connection with the ring gear 21 of the casing of the epicyclic wheel 16 and is in a neutral state. Clutch D with a wide inner ring of clutch 28 connects ring gear 19 of carrier 15 to ring gear 18 of the epicyclic wheel 16. When two PM links are stationary relative to each other, it blocks - all three links rotate at the same frequency. This state of the PM in the radiation diagram is represented by vertical rays - U = 1.0.

 The torque to the PM is transmitted as in first gear, then directly through the PM and further by gears 18 and 19, the clutch D to the gear ring 20 and the output shaft of the unit 5.

 On the beam diagram, this transmission is represented by three rays: the first two rays I and III correspond to the first transmission, and the third ray is directed vertically up to point 5.

Sixth gear
Switch clutch A to the right position.

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

 On the radiation diagram of this transfer correspond to rays II, III and U = 1,0.

Seventh gear
We move couplings A and B to the left - to the second gear position. Before PM, the torque is transmitted as in second gear, then as in the last two gears. In the beam diagram, beam I with an inclination to the right downward and vertical rays II and U = 1.0 characterize this transmission.

Eighth gear - direct
Move clutch A to the right.

 Before PM, the torque is transmitted as in fourth gear, then as in the last three gears.

 In the beam diagram, this transmission is represented by one vertical beam U = 1.0 from t.0 to t.8.

Reverse gears are provided by the PM when switching couplings C and D to position I - while clutch C connects the gear ring 23 of the carrier 15 to the gear ring 24 of the inner wall of the unit body 1 and stops the carrier, the coupling D connects the gear ring 18 of the epicyclic wheel 16 to the gear ring 20 of the output shaft of the unit 5. PM operates in the mode U _ab ^h = -K, the sun gear 13 satellites 14 mounted on the axes of the stopped carrier 15, slowly rotates the epicyclic wheel 16 in the opposite direction.

First Reverse - 1R
We install couplings A and B in the first gear position for forward movement, and couplings C and D in position I (see figure 2 - table below, right).

 Before PM, the torque is transmitted as in the first forward gear, then from the sun gear 13 by satellites 14 to the epicyclic wheel 16, then through the tubular shaft 17, gear ring 18, clutch D, gear ring 20 to the output shaft of the unit 5.

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

Second Reverse - 2R
Switch clutch A to the right position.

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

On the beam diagram, this transmission corresponds to three rays: II, III, and U _ab ^h = -K.

Third Reverse - 3R
We switch couplings A and B to the left position.

 Before PM, the torque comes in both the third forward gear, then - as in the last two gears.

On the beam diagram, three rays I, II and U ^h _ab = -K characterize this transmission.

Fourth Reverse - 4R
Move clutch A to the right position.

 Before PM, the torque is transmitted directly as in the fourth forward gear, then as in the last gears.

A gentle beam U _ab ^h = -K from t.0 to T.4R represents 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.

 The operational capabilities of the vehicle are improved by increasing the number of forward gears of seven to eight and reverse gears from one to four with convenient gear changes and increased efficiency with the exception of the summing mode of operation of the PM.

Claims (1)

A gearbox comprising an aggregate housing in which a three-shaft coaxial gearbox with three pairs of interlocked gears of external gearing is located, gears on the primary and secondary shafts of the gearbox are mounted freely, between them are two gearshift clutches, gears on the intermediate shaft are combined into a block, at the output of this gearbox there is a simple three-link planetary mechanism with a carrier, satellites, a sun gear and an epicyclic wheel, primary, secondary gear shafts, a water output shaft la and the output shaft of the unit are coaxial, the body of the epicyclic wheel, the output shaft of the carrier and the output shaft of the unit have adjacent gears, a gear clutch is installed on the gear rim of the output shaft of the unit, characterized in that the sun gear of the planetary gear is mounted on the secondary shaft of the coaxial gearbox, the body of the epicyclic wheel and the tubular drive shaft of the carrier have adjacent gear rims, next to them on the inner wall of the unit housing is a gear rim on which A switching clutch is installed by a torch, interconnected by a slider with a switching clutch of the output shaft of the unit, the inner rim of which has an increased width.

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