RU2626775C1 - Coannular gearbox with two clutches - Google Patents

Abstract

FIELD: automotive engineering.

SUBSTANCE: two gears clutch and pinions coupled to the pinions of the tubular input shaft, the direct and reverse drive clutch and the two pinions combined in the block are located in the gearbox on the intermediate shaft. One of the pinions is connected with a single pinion of the one-piece input shaft. The other pinion is connected with a pinion freely installed on the output shaft, which is integrated into the block with the reverse gear drive pinion, which is coupled to the driven pinion via an intermediate pinion or via a pinion combined with an intermediate pinion to a block of two pinions. Between the two adjacent pinions coupled to the pinions of the input shafts, the master clutch connecting them can be installed.

EFFECT: high degree of unification and reduced costs for production and repair.

14 cl, 14 dwg

Description

The invention relates to transport machinery, in particular to automated transmissions.

A known gearbox with two multi-plate clutches, containing two coaxial drive shafts located one inside the other, with even and odd gears mounted on them, engaged with permanent gears of the corresponding gears, which can be rigidly connected using synchronizers with driven shafts ( Ivanov A.N., Solntsev A.N., Gaevsky V.V. et al. Fundamentals of the design of a car. - M.: “Book Publishing House” “3a Rulem” LLC, 2005. - 166 pp., Ill.).

A known design variant of the coaxial nine-speed gearbox (KP) with two clutches (see patent US 20070214904 A1, from 20.09.2007).

The design variant of the gearbox consists of a housing with coaxial input and output shafts located in it and an intermediate shaft parallel to them. Two input shafts, one-piece and tubular, are coaxial, located one inside the other and two gears of constant engagement are fixed on the tubular shaft, coupled to the gears of the intermediate shaft, between which an engagement clutch is installed. An additional five pairs of gears are installed on the output and intermediate shafts, and between them are three clutch clutches, including a clutch connecting the entire input shaft to the output shaft, providing direct transmission. A half-clutch is installed on the intermediate shaft, connecting the block of three gears with the shaft, and the other half-clutch of reverse gear is located on a separate axis along with two gears, which are necessaryly coupled to gearbox gears.

The disadvantage of the gearbox is the increased number of couplings (6) and gears (16) to obtain 9 forward gears. And also, in the framework of the patent, modification paths aimed at changing the number of gears and / or gear ratio range are not indicated.

The aim of the invention is a basic fragment of the design of a coaxial gearbox with two clutches, allowing to obtain on its basis design options for multi-stage gearboxes with the possibility of further modification - increasing the number of gears and gear ratios.

This goal is achieved by the fact that on the intermediate shaft there is a clutch for engaging two gears and gears coupled to gears of a tubular input shaft, a clutch for engaging direct or reverse gears and two gears combined in a block and one of them is coupled to a single gear of a whole input shaft, and the other is coupled to a gear freely mounted on the output shaft, combined into a unit with a reverse gear, which is coupled to the driven via an intermediate gear or via a gear, from the intermediate to the block of two gears.

It is also possible that a gear coupled to the gear is fixed to the intermediate shaft, to which the sun gear of the planetary demultiplier is rigidly connected, having an upper or lower range clutch and a carrier mounted on the output shaft.

It is also possible that at least one range engagement clutch and two gears coupled to gears fixed to the countershaft are arranged on the output shaft.

It is also possible that at least one additional range clutch and a gear coupled to the gear rigidly connected to the output shaft are arranged on the intermediate shaft.

It is also possible that the outer gear of the output shaft is rigidly connected by the clutch with the planet carrier of the planetary gear having a clutch of the upper or lower range and the sun gear mounted on the output shaft.

It is also possible that on the intermediate shaft there is a clutch and a gear coupled to the gear rigidly connected to the planet carrier of the planetary gear having a higher or lower range clutch and a sun gear mounted on the output shaft.

It is also possible that at least one range engagement clutch and two gears coupled to gears fixed to the output shaft are arranged on the intermediate shaft.

It is also possible that at least one additional range clutch and a gear coupled to the gear fixed to the countershaft are located on the output shaft.

It is also possible that a gear coupled to the gear is fixed on the countershaft, which is tightly connected by the clutch on to the planet carrier of the planetary gear having a clutch on the upper or lower range and a sun gear mounted on the output shaft.

It is also possible that on the intermediate shaft there is a clutch and a gear coupled to the gear rigidly connected to the planet carrier of the planetary gear having a higher or lower range clutch and a sun gear mounted on the output shaft.

It is also possible that the range engagement clutch and two gears are located on the intermediate shaft, moreover, one of them is engaged with the gear rigidly connected to the output shaft, and the other is engaged with the gear gear rigidly connected to the planet carrier of the planetary demultiplier having a higher or lower range and sun gear mounted on the output shaft.

It is also possible that on the output shaft, next to the reverse gear, are located at least one additional range clutch and gear engaged with the gear rigidly connected to the countershaft.

It is also possible that on the intermediate shaft, next to the reverse gear, are located at least one additional range clutch and gear engaged with the gear rigidly connected to the output shaft.

It is also possible that between two adjacent gears coupled to the gears of the input shafts, an inclusion clutch connecting them is installed.

In FIG. 1 shows a kinematic diagram of a basic fragment of a coaxial gearbox design with two clutches, corresponding to paragraph 1 of the claims.

In FIG. 2 shows a kinematic diagram of a design variant of a CP with a base fragment, according to paragraphs 2 and 14 of the claims.

In FIG. 3 is a beam diagram of the KP shown in FIG. 2. On the horizontal are the numbers of the various gears. Logarithms and gear ratios are shown on the lower scale. A beam pointing to the right indicates a deceleration. The better the beam, the greater the gear ratio. A beam pointing to the left indicates an accelerating gear. For a better understanding, the ray represented by the dashed line indicates reverse gear, and the dash-dot ray indicates a downshift.

In FIG. 4 shows a kinematic diagram of a design variant of a 9 or 7-speed gearbox according to claim 3.

In FIG. 5 is a beam diagram of a 9-speed gearbox.

In FIG. 6 shows a kinematic diagram of an embodiment of a 7-speed reduction gearbox according to claim 3.

In FIG. 7 is a beam diagram of a 7-speed gearbox with a reduction gear.

In FIG. 8 shows a kinematic diagram of a design variant of a 17 or 13-speed gearbox according to claim 5.

In FIG. 9 is a beam diagram of a 17-speed gearbox.

In FIG. 10 is a beam diagram of a 13-speed gearbox.

In FIG. 11 shows a kinematic diagram of a design variant of a 17 or 15-speed gearbox according to claim 9.

In FIG. 12 is a beam diagram of a 17 or 15 speed gearbox.

In FIG. 13 shows a kinematic diagram of an embodiment of a 15 or 13-speed manual gearbox or a 13-speed manual gearbox with two reduction gears according to claim 11.

In FIG. 14 is a beam diagram of the KP shown in FIG. 13.

The composition shown in FIG. 1, the kinematic diagram of the base fragment includes installed in the bearings of the housing 1: two coaxial input shafts 2 and 3 located one inside the other, an output shaft 4 mounted coaxially with them and an intermediate shaft parallel to them 5. The gears 6 and 7 are rigidly fixed to the input shaft 2 and engaged with gears 8 and 9 freely mounted on the countershaft 5, respectively. Gears 10 and 11 are loosely mounted on countershaft 5 and combined into a block. The gear 10 is coupled to a single, rigidly mounted gear 12 of the entire input shaft 3. The gear 11 is coupled to a gear 13 freely mounted on the output shaft 4, combined into a block with a reverse gear 14, which is engaged with the driven gear 15 through an intermediate gear 16, which are installed, respectively, on the intermediate shaft 5 and a separate axis 17. Clutches A (18) and B (19) are located on the intermediate shaft 5, between gears 8-9 and 11-15, respectively. The clutch C (20) is located on the output shaft 4 between the gears 12 and 13. The driven disk 21 of the left clutch (L) is installed on the input shaft 3, and the driven disk 22 of the right clutch (P) is installed on the input shaft 2.

The composition shown in FIG. 2, the kinematic diagram of a design variant of a 10 or 8-speed gearbox includes the same details as the base fragment composition discussed above and additionally: gear 23 is fixed to the intermediate shaft 5 and engaged with gear 24 freely mounted on the output shaft 4, combined into the block with the sun gear 25 of the planetary demultiplier. A carrier 26 of the demultiplier is fixed on the output shaft 4, and the hub of the coupling D is rigidly connected to its epicyclic gear 27 (28). A gear ring 29 is fixed on the gearbox housing 1, and a gear ring 30 is mounted on the gear 24. The hub of the coupling E (31) is fixed on the gear 10.

The composition shown in FIG. 4, the kinematic diagram of a design variant of a 9 or 7-speed gearbox, includes the same details as that of the base fragment considered above and additionally: gears 32 and 33 are mounted on the intermediate shaft 5 and engaged with gears 34 freely mounted on the output shaft 4 and 35, respectively, and between them a clutch of inclusion of ranges F (36) is installed.

The composition shown in FIG. 8, the kinematic diagram of the design variant of the 17 or 13-speed gearbox includes the same details as the previous structure of the 9 or 7-speed gearbox and additionally: the sun gear 37 of the planetary gear box is fixed to the output shaft 4, and with its epicyclic gear 38 the hub of the coupling D (39) is rigidly connected. A gear rim 40 is fixed on the gearbox housing 1, and gear rims 42 and 43 are mounted on the gear carrier 41 of the demultiplier. The coupling hub K is rigidly connected to gear 35 (44). Drove 41 demultiplicator mounted on the shaft 45 of the drive of the drive wheels.

The design fragment proposed by this invention allows to obtain multi-stage gearbox variants with a planetary gearbox (demultiplicator), a gear gearbox and a combined version using both types of said gearboxes. Therefore, in view of the need for a summary, but with the completeness sufficient for the implementation of the invention, the operation of the base fragment shown in FIG. 1, consider an example of a design for a gearbox with a planetary gear (see FIG. 2), a design with a gear reducer (see FIG. 4), and a variant with a combined gear (see FIG. 8).

The operation of the gearbox shown in FIG. 2 is carried out as follows.

Downshift

We turn on the left clutch (L), we transfer couplings A and E to the left position. The clutch D is switched to the right position, while the epicyclic wheel 27 of the planetary demultiplier through the clutch D and the ring gear 29 is rigidly connected to the gearbox housing 1. The torque from the input shaft 3 through a pair of coupled gears 12-10, clutch E, a pair of gears 9-7, shaft 2, a pair of gears 6-8 and clutch A, is transmitted to the intermediate shaft 5, a pair of gears 23-24, sun gear 25 and further, according to the prior art of the planetary demultiplier, from carrier 26 to the output shaft 4.

On the radiation diagram (see Fig. 3), this transmission is reflected by the ray 0-II and then sequentially connected by dot-dash rays: tilted left up II-III, tilted right II-III-I, vertical down and tilted right to the letter P.

1st and 3rd gear

They are carried out in a manner that is understandable to a specialist by transmitting torque with the right clutch (P) to the input shaft 2, in pairs of gears 6-8 (1st gear), 7-9 (3rd gear) and clutch A, located in the left (1st gear) or right (3rd gear) ) position, on the intermediate shaft 5 and further similarly to the transmission considered above.

In the radiation diagram (see Fig. 3), 1 transmission is reflected in series with connected beams: 0-I, with a vertical beam down and inclined to the right to digit 1. 3 transmission is reflected in series with beams: 0-III, with a vertical beam down and inclined to the right to number 3.

2nd gear

It is carried out by transferring the torque with the left clutch (L) to the input shaft 3 by a pair of gears 12-10 and the clutch B, in the left position, on the intermediate shaft 5. Further, similarly to the operation of the gearbox in a lower gear, discussed above.

On the radiation diagram (see Fig. 3), this transmission is reflected in series connected beams: 0-II, vertical down and inclined to the right to the number 2.

4th gear

It is carried out by transferring the torque with the left clutch (L) to the input shaft 3, a pair of gears 12-10, a block of gears 10-11, a pair of gears 11-13 and a clutch C, located in the right position, on the output shaft 4. During operation of the gearbox on In this gear, while continuing to increase the engine speed and vehicle speed, clutch D switches to the left position. As a result, the planetary demultiplier is blocked - the epicyclic wheel 27 through the clutch D and the ring gear 30 is rigidly connected to the gear 24 and the sun gear 25.

On the beam diagram (see Fig. 3), this transmission is reflected in series connected beams: 0-II, inclined to the right and vertical down to the number 4.

5th, 6th and 7th gear

They are carried out similarly to the work of the gearbox in 1st, 2nd and 3rd gears, respectively, considered above, but with a locked planetary gearbox. On the radiation diagram (see Fig. 3), these transmissions are reflected in series with connected beams: 5th gear - tilted to the right 0-I and vertical down to the number 5; 6 gear oblique to the right 0-II and vertical down to the number 6; 7, the gear is oblique to the right 0-III and vertical down to the number 7.

8 (direct) transmission

It is carried out by transmitting torque with the left clutch (L) to the input shaft 3, clutch C, in the left position, to the output shaft 4. During gearbox operation in this gear, while continuing to increase the engine speed and vehicle speed, clutch E switches to the left position.

On the beam diagram (see Fig. 3) this transmission is reflected by a vertical beam O-8.

9 gear

We engage the right clutch (P) of the clutch C and E in the left position. Torque from the input shaft 2 through a pair of coupled gears 7-9, clutch E, a pair of gears 10-12 and clutch C is transmitted to the output shaft 4.

In the beam diagram (see Fig. 3), this transmission is reflected in series by connected beams 0-III, inclined to the left upward by III-II and vertically downward to the number 9.

Reverse

We turn on the left clutch (L), clutches B and D in the right position. The torque from the input shaft 3 through a pair of coupled gears 12-10, a block of gears 10-11, a pair of gears 11-13, a block of gears 13-14, gears 14-16-15 and a clutch B is transmitted to the intermediate shaft 5, a pair of gears 23 -24, the sun gear 25 and beyond, according to the prior art of the planetary demultiplier operation, from carrier 26 to the output shaft 4.

On the radiation diagram (see Fig. 3), this transmission is reflected by the ray 0-II and then sequentially connected by rays from the dashed line to the letters ZX.

The operation of the 9-speed gearbox shown in FIG. 4 is carried out as follows.

1st gear

We turn on the right clutch (P), switch clutches A and B to the left position, and clutch F to the right. Torque from the input shaft 2 through a couple of coupled gears 6-8, clutch A is transmitted to the intermediate shaft 5, a pair of gears 33-35, the clutch F and the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series by the connected beams 0-I, I-1.

2nd gear

We turn on the left clutch (L), clutch B in the left position, switch clutch A to the right position. Torque from the input shaft 3, a pair of gears 12-10, clutch B is transmitted to the intermediate shaft 5, a pair of gears 33-35, the clutch F and the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series connected by beams 0-II, II-2.

3rd gear

We turn on the right clutch (P), clutch A in the right position, turn off clutch B, and switch clutch C to the right position. Torque from the input shaft 2 through a pair of gears 7-9, clutch A is transmitted to the intermediate shaft 5, a pair of gears 33-35, the clutch F and the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series by connected beams 0-III, III-3.

4th gear

We turn on the left clutch (L), clutch C in the right position, switch clutches A and F to the left position. The torque from the input shaft 3, a pair of gears 12-10, a block of gears 10-11, a pair of gears 11-13 and a coupling C is supplied to the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series by beams 0-II, II-4.

5 gear

We turn on the right clutch (P), clutches A and F in the left position, turn off clutch C, and switch clutch B to the left position. Torque from the input shaft 2 through a pair of coupled gears 6-8, clutch A is transmitted to the intermediate shaft 5, a pair of gears 32-34, the clutch F and the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series by the connected beams 0-I, I-5.

6th gear

We turn on the left clutch (L), clutch B in the left position, switch clutch A to the right position. Torque from the input shaft 3, a pair of gears 12-10, clutch B is transmitted to the intermediate shaft 5, a pair of gears 32-34, the clutch F and the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series by connected beams 0-II, II-6.

7th gear

We turn on the right clutch (P), clutch A in the right position, turn off clutch B, and switch clutch C to the left position. The torque from the input shaft 2 through a pair of gears 7-9, clutch A, the intermediate shaft 5, a pair of gears 32-34 and the clutch F enters the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series connected by beams 0-III, III-7.

8 (direct) transmission

We turn on the left clutch (L), clutch C in the left position, clutch A in the right position. The torque from the input shaft 3 by the clutch C is transmitted to the output shaft 4. During the gearbox operation in this gear, while continuing to increase the engine speed and vehicle speed, the clutch F is turned off and the clutch B switches to the left position.

On the radiation diagram (see Fig. 5), the eighth gear is reflected by point 0 / number 8.

9 gear

We engage the right clutch (P) of the clutch C and B in the left position, clutch A in the right position. The torque from the input shaft 2 through a pair of gears 7-9, clutch A, clutch B, a pair of gears 10-12 and clutch C is transmitted to the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series by beams 0-III, III-9.

Reverse

We turn on the left clutch (L), clutches B and F in the right position. The torque from the input shaft 3 through a pair of gears 12-10, a block of gears 10-11, a pair of gears 11-13, a block of gears 13-14, gears 14-16-15 and a clutch B is transmitted to the intermediate shaft 5, a pair of gears 33- 35 and clutch F to the output shaft 4.

On the radiation diagram (see Fig. 5), this transmission is reflected in series by connected beams 0-II, II-4 and then sequentially connected by beams from a dashed line to the letters ZX.

The operation of the 17-speed gearbox shown in FIG. 8 is carried out as follows.

1-8 gears, reverse

They are carried out similarly to the work of the 9-speed gearbox in 1-8 gears described above, respectively, but the torque is transmitted from the output shaft 4 to the sun gear 37 of the planetary demultiplier, in which the epicyclic wheel 38 is connected through gearbox D and gear ring 40 to the gearbox housing 1 . And further, the torque according to the prior art of the planetary demultiplier, comes from the carrier 41 to the shaft 45 of the drive of the drive wheels. During gearbox operation in 8th gear, while continuing to increase the engine speed and vehicle speed, clutch F is turned off, clutch A switches to the left position, and clutch K switches to the right position.

9, 10 and 11 gears

The work of the 9-speed gearbox in 1, 2 and 3 gears, respectively, is carried out similarly, but with gear 35, through the clutch K and gear ring 43, the torque is transmitted to the planet carrier 41 of the planetary gear and the drive shaft 45 of the drive. During gearbox operation in 11th gear, while continuing to increase the engine speed and vehicle speed, clutch D switches to the left position. As a result, the planetary gear is blocked - the epicyclic wheel 38 through the clutch D and the ring gear 42 is rigidly connected to the carrier 41.

12, 13, 14, 15, 16 and 17 gears

Carried out similarly to the above work of a 9-speed gearbox in 4, 5, 6, 7, 8 and 9 gears, respectively, but from the output shaft 4, through a locked planetary gear, the torque is transmitted to the drive shaft 45 of the drive wheel.

The technical result of using the basic fragment of the design of a coaxial gearbox with two clutches is the creation on its basis of multi-stage gearbox design options with the possibility of further modification - increasing the number of gears and gear ratios. At the same time, most of the components and parts of multi-stage gearboxes remain unchanged, which ensures a high degree of unification and a reduction in production and repair costs.

In the given examples of the design options for the coaxial gearbox, gears with variable inclusion of two clutches are considered. Also, sequential gears with operation on the same clutch are possible, but they are not indicated and are not considered.

The kinematic diagrams show only some of the possible options for a multi-stage gearbox with two clutches. At the same time, KP can be in a single version of the design, but with the indicated features, essential and interconnected, forming a stable set of essential features sufficient to obtain a technical result.

Claims (14)

1. Coaxial gearbox with two clutches, comprising a double clutch assembly, a housing with coaxial input and output shafts disposed therein and an intermediate shaft parallel to them, with permanent gears mounted thereon, which can be rigidly connected using shafts with shafts, this, two input shafts, one-piece and tubular, are coaxial, located one inside the other and two or three gears are fixed on the tubular shaft, and a coupling is connected to the output shaft connecting to the output shaft an integral input shaft or a freely mounted gear, characterized in that on the intermediate shaft there are a two-gear clutch and gears coupled to the tubular input shaft gears, a forward or reverse gear clutch and two gears combined into a block and one of them is coupled to a single gear of a single input shaft, and the other is coupled to a gear freely mounted on the output shaft, combined in a block with a reverse gear, which is coupled to the driven via hydrochloric or via pinion gear combined with two intermediate gear unit. 2. Coaxial gearbox with two clutches according to claim 1, characterized in that a gear is fixed to the intermediate shaft, coupled to the gear, to which the sun gear of the planetary demultiplier is rigidly connected, having an upper or lower range clutch and a carrier mounted on the output shaft . 3. Coaxial gearbox with two clutches according to claim 1, characterized in that at least one range engagement clutch and two gears coupled to gears fixed to the intermediate shaft are located on the output shaft. 4. Coaxial gearbox with two clutches according to claim 3, characterized in that at least one additional range clutch and a gear engaged with the gear are rigidly connected to the output shaft and are located on the intermediate shaft. 5. Coaxial gearbox with two clutches according to claim 3, characterized in that the final gear of the output shaft rigidly connects the clutch to the planet carrier of the demultiplier, which has a clutch of upper or lower range and a sun gear mounted on the output shaft. 6. Coaxial gearbox with two clutches according to claim 3, characterized in that on the intermediate shaft there are an engagement clutch and a gear engaged with a gear rigidly connected to the planet carrier of the planetary gearbox having an engagement clutch of a higher or lower range and a sun gear fixed to output shaft. 7. Coaxial gearbox with two clutches according to claim 1, characterized in that at least one range clutch and two gears coupled to gears fixed to the output shaft are located on the intermediate shaft. 8. Coaxial gearbox with two clutches according to claim 7, characterized in that at least one additional range clutch and a gear coupled to the gear fixed to the intermediate shaft are located on the output shaft. 9. The coaxial gearbox with two clutches according to claim 7, characterized in that a gear coupled to the gear is fixed to the intermediate shaft, which is tightly connected by the clutch to the planet carrier of the demultiplier having a clutch of higher or lower range and a sun gear fixed to output shaft. 10. Coaxial gearbox with two clutches according to claim 7, characterized in that on the intermediate shaft there are an engagement clutch and a gear engaged with a gear rigidly connected to the planet carrier of the planetary gearbox having an engagement clutch of a higher or lower range and a sun gear fixed to output shaft. 11. Coaxial gearbox with two clutches according to claim 1, characterized in that on the intermediate shaft there is a range clutch and two gears, moreover, one of them is coupled to the gear rigidly connected to the output shaft, and the other is rigidly coupled to the gear associated with a planetary planetary gear carrier having an upper or lower range clutch and a sun gear fixed to the output shaft. 12. Coaxial gearbox with two clutches according to claim 11, characterized in that at least one additional range engagement clutch and gear engaged with the gear rigidly connected to the intermediate shaft are located on the output shaft, next to the reverse gear . 13. Coaxial gearbox with two clutches according to claim 11, characterized in that at least one additional range engagement clutch and gear engaged with the gear rigidly connected to the output shaft are located on the intermediate shaft, next to the reverse gear . 14. Coaxial gearbox with two clutches according to one of paragraphs. 1-13, characterized in that between two adjacent gears coupled to the gears of the input shafts, an engaging clutch is installed connecting them.

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