RU2531995C1 - Gearbox - Google Patents

Abstract

FIELD: transport.

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

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

4 cl, 4 dwg, 1 tbl

Description

The invention can be used in transmissions of vehicles and is intended for stepwise changes in speed and torque.

Currently, gearboxes of vehicles are being improved in the direction of increasing the number of stages while striving to reduce the number of gear pairs and controls used, which allows to increase the efficiency of the gearbox and improve overall dimensions.

The invention is known - a gearbox with two clutches, for example [Patent DE 19821164 Doppelkupphmgsgetriebe from 11/18/1999]. Pairs of gears located on the intermediate shafts of gearboxes of this type are connected to the shafts using couplings. And the intermediate shafts are alternately connected to the shaft of the power source using two friction clutches. Such a branched arrangement allows for the preliminary preparation of the next stage immediately prior to its inclusion by connecting an unloaded intermediate shaft with a gear pair of the next gear. After that, one clutch is turned off, and the second is turned on, which allows switching almost without breaking the power flow. Couplings have three positions: 1) free rotation; 2) the connection of the shaft with the gear pair on the left; 3) the connection of the shaft with the gear pair on the right.

The gearbox in question has six forward gears and one reverse gear, with two clutches, three clutches with three positions and one clutch with two positions. A significant drawback of gearboxes with two clutches is that each stage is implemented by a separate gear pair when the corresponding clutch is engaged. As a result, each additional step leads to an increase in the number of mechanisms and controls used, as well as to an increase in the overall dimensions and mass of the structure.

Differential gearboxes consisting of planetary gears are known. The number of stages in them is determined by the number and type of planetary mechanisms, as well as the number of controlled clutches and brakes. For example, a 6-speed gearbox (patent US 6729990 Automatic Gearbox dated 05/04/2004) has 3 clutches, 2 brakes and consists of the so-called Ravinier gearbox and a single-row planetary gear. And the design of the 7-speed gearbox (US patent 6302820 Planetary Speed Change Transmission dated October 16, 2001) contains 2 clutches, 4 brakes, 1 freewheel, Ravigne gearbox and two single-row planetary gears. An 8-speed gearbox (patent WO 2006/074707 Multispeed Transmission dated 07.20.2006) uses 3 clutches, 2 brakes and 4 single-row planetary gears. 9-speed planetary gearbox (ZF Friedrichshafen Brochure: "Heading for a whole new dimension" http://www.zf.com/corporate/en/products/innovations/9hp_automatic transmission / 9hp_auto matic transmission.html accessed 02.20.2013) contains 3 clutches, 3 brakes and as many single-row mechanisms as the 8-speed one, in order to reduce the overall dimensions of the gearbox, two of them are arranged one above the other.

Thus, with an increase in the number of steps, the number and complexity of the mechanisms used increases and the number of controls increases.

A gearbox known in JP 4425208 (03/03/2010) is proposed as the closest prototype. It allows you to get six steps forward, one reverse stage using 6 controls (four clutches and two brakes). This device contains a stationary housing, input and output differentials, each of which is composed of interacting links: the sun wheel, epicycle and carrier, carrying satellites; input link connected to the input differential differential sun wheel, output link, gears, controlled couplings, shafts connected to differential links, and kinematic couplings between shafts, included using controlled couplings.

The problem to which the invention is directed is the creation of a compact gearbox, in which with a small number of gear pairs and controlled clutches, a greater number of stages are achieved.

The technical result achieved by the implementation of the invention is to improve the operational characteristics of the gearbox by expanding the range of gear ratios, increasing efficiency, reducing metal consumption and overall dimensions of the structure.

The specified technical result in a gearbox containing a fixed housing, input and output differentials, each of which is composed of interacting links: a sun wheel, an epicycle and a carrier that carries satellites; input link connected to the input differential sun gear, output link, gears, controlled couplings, shafts connected to differential links, and kinematic couplings between shafts included by controlled couplings, is achieved by the fact that it contains a spurious gear and controlled lock couplings for connecting the epicycle with the carrier of the input differential and the epicycle with the sun wheel of the output differential, and kinematic connections are made between the shaft of the epicycle of the input differential and fixed to the case between the input differential epicyclic shaft and the output differential sunshine shaft through a spurious gear, between the input differential carrier shaft and the output differential sunshine shaft, between the output differential sunshine shaft and the stationary housing, between the output differential epicyclic shaft and the stationary housing, between the shaft drove the input differential and the epicyclic of the output differential, the carrier of which carries satellites in the form of single gears and is connected to the output link.

Kinematic connections between the shafts can be made in the form of constantly engaged gears mounted on the shafts.

Kinematic relationships between the input differential epicyclic shaft and the output differential sunshine shaft, the input differential differential carrier shaft, and the shafts of the output differential sun gear and the output differential epicyclic shaft may contain additional shafts with gear wheels fixed to them.

Managed couplings can be made with three fixed positions, providing free rotation of the shaft, the connection of the shaft with the gear wheel, the connection of the shaft with a fixed housing.

The invention is illustrated by drawings. Figure 1 presents a variant of the layout of the claimed gearbox, in which the differentials and, accordingly, the input and output links are not aligned, and the rotation of the input and output links are multidirectional on the forward steps. Figure 2 presents a variant of the gearbox, in which the differentials, input and output links are aligned, and their rotation coincides in direction. Figure 3 - layout of the gearbox according to the scheme of figure 1, in which the clutch has three fixed positions. Similarly, figure 4 shows the layout of the gearbox according to the scheme of figure 2 with controlled clutches having three positions.

The gearbox contains: a fixed housing 1, an input differential 2, composed of interacting links: the sun wheel 3, epicycle 4 and carrier 5 with satellites 6; output differential 7, composed of interacting links: the sun wheel 8, epicycle 9 and drove 10 with satellites 11, made in the form of single gears; an input link 12 connected to the sun wheel 3 of the input differential 2; output link 13 connected to the carrier 10 of the output differential 7; shafts 14, 15, 16 and 17, respectively connected to the epicycle 4, the carrier 5 of the input differential 2 and the sun wheel 8 and the epicycle 9 of the output differential 7.

The kinematic connection between the shaft 14 of the epicycle 4 of the input differential 2 and the fixed housing 1 is realized by a controlled clutch 18A, and between the same shaft 14 and the shaft 16 of the sun wheel 8 of the output differential 7 are gears 19, 20, a spurious gear 21 and a controlled clutch 18B (Fig. .13). The kinematic connection between the shaft 15 of the carrier 5 of the input differential 2 and the shaft 16 of the sun wheel 8 of the output differential 7 contains a controlled coupling 22B and gears 23 and 24, and the coupling 16A of the shaft 16 is connected to the housing 1. The kinematic connection between the shaft 17 of the epicycle 9 of the output differential 7 and the shaft 15 of the carrier 5 of the input differential 2 includes a controlled clutch 25B and gears 26, 27. The coupling 25A of the shaft 17 of the epicycle 9 of the output differential 7 is connected to the stationary housing 1. The gearbox also contains controlled locking clutches 28 and 2 9, connecting respectively the epicycle 4 with the carrier 5 of the input differential 2 through the shafts 14, 15 and the sun wheel 8 with the epicycle 9 of the output differential 7 through the shafts 16 and 17.

In the gearbox diagrams of FIG. 1 and FIG. 3, the above kinematic connections are made in the form of gears permanently engaged, mounted on respective shafts.

In the diagrams of the gearbox of figure 2 and figure 4, the kinematic relationship between the shaft 14 of the epicycle 4 of the input differential 2 and the shaft 16 of the sun wheel 8 of the output differential 7, as well as between the shaft 15 of the carrier 5 of the input differential 2 and the shafts 16, 17 of the sun wheel 8 and epicycle 9 of the output differential 7 contain additional shafts 30 and 31 with gears 32, 33 and 34 fixed to them.

In the gearbox diagrams of FIG. 1 and FIG. 2, two-position controlled clutches 18A, 18B, 22A, 22B, 25A, 25B, 28, and 29 with a total number of independent states equal to 16 are used to turn on the kinematic connections and the corresponding steps. To reduce the total the number of couplings, reducing losses in idle clutches, simplifying their condition monitoring and gearbox control algorithm, it is advisable to use three couplings instead of the first six of these two-position clutches, each of which has three fixed positions, providing rim rotation of the shaft (state N), connection of the shaft to the gear wheel (B), connection of the shaft to the fixed housing (A). In this case, the total number of controlled couplings will decrease from 8 to 5, and the number of their independent states will be reduced to 13.

The location of the three-position clutch on the shafts of the inventive gearbox is shown in figure 3 and figure 4. Here, the couplings 18A and 18B are replaced by a three-position clutch 18; couplings 22A and 22B with clutch 22, and couplings 25A and 25B with clutch 25.

It is important to note that in gearboxes with fixed axles of the wheels, the parasitic gear is used to reverse the directions of rotation of the shafts and obtain reverse gears. In the inventive gearbox, the spurious gear 21 is used for both forward and reverse gears. In the proposed kinematic scheme of the gearbox, reverse gear can be obtained only with the simultaneous inclusion of clutches 18B and 28. In this case, the differential 2 is blocked, rotates as a whole, and the direction of rotation of the output link changes to the opposite.

The claimed gearbox allows you to get 13 forward gears and 2 reverse gears. It has four degrees of freedom, that is, for the implementation of each stage, three controls must be simultaneously included.

The gearbox operates (Figs. 1, 3) as follows (only included clutches are indicated, unspecified clutches are not included or are in state N):

- first stage: couplings 18B, 22B, 25A are included. Differential 2 distributes the input power flow between the epicycle 4 and the carrier 5. The summation of the flows occurs on the shaft 16, then the movement is transmitted to the sun wheel 8 and through the differential 7, which works as a gearbox with the stopped epicycle 9, to the output link 13;

- second stage: couplings 18A, 25A, 22B are included. Both differentials work like gears with stopped epicycles. The rotation from the input link 12 is transmitted sequentially to the shaft 15, the gears 24 and 23 to the sun wheel 8 and then to the output link 13;

- third stage: clutches 18В, 22В and blocking clutch 29 are included. Differential 2 distributes the input power flow between epicycle 4 and carrier 5. Summing the flows occurs on shaft 16, then the movement is transmitted to the blocked differential 7, rotating as a whole;

- fourth stage: clutches 18V, 22V and 25V are included. Differential 2 distributes the input power flow, and differential 7 summarizes. All available gears and shafts are involved, the transmission of motion occurs in parallel through all links of the gearbox;

- fifth stage: clutches 25A, 22B and a lock clutch 28 are included. In this case, differential 2 is blocked and rotates as a whole, then the rotational movement is transmitted through gears 24 and 23 to differential 7, which works as a gearbox with the stopped epicycle 9;

- sixth stage: clutches 18A, 22B and lock-up clutch 29 are included. Differential 2 works as a gearbox with the epicycle 4 stopped. The carrier 5 connected to the shaft 15 transmits the movement through gears 24 and 23 to the differential 7 locked and rotating as a whole;

- seventh step: couplings 18A, 22A and 25B are included. Differentials 2 and 7 work as gears, the first with the stopped epicycle 4, and the second with the stopped sun wheel 8. The transmission of movement is carried out through carrier 5, gears 26, 27 and epicycle 9;

- eighth step: couplings 22B, 25B and 18A are included. Differential 2 works like a gearbox, and differential 7 summarizes two power flows separated on shaft 15;

- ninth stage: clutches 18A, 25B and blocking clutch 29 are included. Differential 2 works as a gearbox with the epicycle 4 stopped. The carrier 5, connected to the shaft 15, transmits movement through gears 24 and 23 to the differential 3 locked and rotating as a whole;

- tenth step: clutch 22B and both locking clutches 28 and 29 are engaged. Both differentials are locked and rotate as a whole, the transmission of movement between them is carried out through gears 24 and 23;

- eleventh step: clutches 22A, 25B and blocking clutch 28 are included. Differential 2 is blocked, transmission of movement occurs through gears 26 and 27 to epicycle 9 of differential 7, which works as a gearbox with the sun wheel 8 stopped;

- twelfth stage: clutches 22B, 25V and blocking clutch 28 are included. Differential 2 is blocked, input power flow is transmitted to shaft 15, divided and passes through gears 24, 23 and 26, 27, and then summed up on differential 7;

- thirteenth step: clutch 25B and both blocking clutches 28 and 29 are turned on. Differentials 2 and 3 are locked and rotate as a whole, the transmission of movement between them is carried out through gears 26 and 27;

- the first reverse gear: clutches 18B, 25A and blocking clutch 28 are included. Differential 2 is locked and rotates as a whole, the direction of rotation of the epicycle 4 in this case coincides with the direction of rotation of the sun wheel 3. The direction is reversed using a parasitic gear 21. Differential 3 works as a reducer with the stopped epicycle 9;

- second reverse gear: clutch 18B and lock-up clutches 28 and 29 are engaged. Both differentials are locked and rotate as a whole, the transmission of movement occurs through gears 19 and 20 with spurious gear 21. The steps are implemented by the gearbox depending on the controls included ( are shown by the sign “x”) are tabulated. R1 and R2 in the table indicate reverse gears.

Step number Control Status Gear ratio eighteen 22 25 28 29th "BUT" "B" "BUT" "AT" "BUT" "AT" one x x x 27.8 2 x x x 12.0 3 x x x 9.3 four x x x 6.0 5 x x x 4.8 6 x x x 4.0 7 x x x 3.3 8 x x x 2.6 9 x x x 2.2 10 x x x 1,6 eleven x x x 1.3 12 x x x 1,0 13 x x x 0.9 R1 x x x 10.6 R2 x x x 3,5

In the right column of the table shows the results of calculating the gear ratios for each stage with the following ratios between the gears of the gearbox (figure 1, 3):

- -1.5 between the sun wheel 3 and the epicycle 4 when the carrier 5 is stopped;

- 3,528 between the gears 19 and 20 through the spurious gear 21;

- -1.595 between gears 24 and 23;

- -0.873 between gears 26 and 27;

- -2.0 between the sun wheel 8 and the epicycle 9 when the carrier 10 is stopped.

For the kinematic diagrams of the gearbox shown in FIGS. 2 and 4, the above thirteen forward gears and two reverse gears are implemented with the same combination of the included controls. The only difference is that when the corresponding kinematic connections are turned on, the movement is transmitted through additional gear wheels 32, 33 and 34 and shafts 30 and 31.

In contrast to the differential and dual-clutch gearboxes described above, the claimed gearbox has a clear advantage in terms of the number of stages and the number of controls used. It uses only five controls (three couplings with three states and two couplings with two states) to get thirteen forward gears and two reverse gears.

The layout options of the gearbox in figures 1 and 3 are characterized by minimum radial overall dimensions and maximum efficiency, since they contain a minimum number of gear pairs. The efficiency of the options for the layout of the gearbox shown in figure 2, 4 is somewhat lower, but may have a minimum axial overall dimensions and increased torsional rigidity of the shafts due to their reduced length.

An additional advantage of the gearbox is an increase in the gear ratio sequentially from the mechanism to the mechanism even with parallel transmission of power, which guarantees the absence of circulating powers possible in the gearboxes of this type of gears, which lead to a significant increase in the loads on the transmission links, lower efficiency, increased wear of the mechanisms, etc. P.

Claims (4)

1. A gearbox containing a fixed housing, input and output differentials, each of which is composed of interacting links: a sun wheel, an epicycle and a carrier that carries satellites; input link connected to the input differential differential sun gear, output link, gears, controlled couplings, shafts connected to differential links, and kinematic couplings between shafts included by controlled couplings, characterized in that it contains a spurious gear and controlled locking couplings for connections of the epicycle with the carrier of the input differential and the epicycle with the sun wheel of the output differential, and kinematic connections are made between the shaft of the epicyclic of the input differential and the stationary gear a mustache, between the input differential epicyclic shaft and the output differential sunshine shaft through the spurious gear, between the input differential carrier shaft and the output differential sunshine shaft, between the output differential sunshine shaft and the fixed housing, between the output differential epicyclic shaft and the stationary housing, between the shaft drove the input differential and the epicycle of the output differential, the carrier of which carries satellites in the form of single gears and is connected to the output enom. 2. The gearbox according to claim 1, characterized in that the kinematic connections between the shafts are made in the form of constantly engaged gears mounted on the shafts. 3. The gearbox according to claim 1, characterized in that the kinematic connections between the input differential epicyclic shaft and the output differential sun shaft shaft, the input differential gear carrier shaft and the shafts of the solar differential gear and the output differential epicyclic shaft contain additional shafts with gears fixed to them. 4. The gearbox according to claim 1, characterized in that the controlled clutch is made with three fixed positions, providing free rotation of the shaft, the connection of the shaft with the gear wheel, the connection of the shaft with a fixed housing.

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