RU2391588C1 - Gear box - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: gear box consists of fixed case (1), of inlet link (2), of outlet link (3), of planetary mechanism (4), of single shaft (8) and of two-layer shaft (9), of tooth gear and of controlled clutches. Two-layer shaft (9) consists of external shaft (10) and internal shaft (11). Controlled clutch (12) connects internal (11) and external (12) shafts. The tooth gears are mounted on shafts (8, 10, 11) and form pairs (13, 14, 15, 16, 17) continuously engaged and transmitting motion from shaft to shaft by means of controlled clutches (18, 19, 20, 21, 22). Two controlled clutches (23) and (24) join correspondingly internal shaft (11) with fixed case (1) and external shaft (10) with fixed case (1). Carrier (5), sun gear (6) and epicycle (7) of planetary mechanism (4) are connected correspondingly to inlet link (2), internal (11) and external (10) shafts. Single shaft (8) is tied with outlet link (3).

EFFECT: increased reliability and resource of facility operation.

15 dwg, 1 tbl

Description

The invention relates to mechanical engineering, and in particular to mechanisms for step change of speed, and can be used mainly in the automotive industry.

At present, automobile gearboxes are improving in the direction of increasing the number of stages, while striving to reduce the number of gear pairs and controlled couplers, and, as a result, increase the efficiency of the box and improve its overall dimensions.

Two types of automobile gearboxes are known. The first type is planetary gearboxes containing planetary gears, the number of which determines the number of gearbox steps. An example is a gearbox, known from patent WO 2006/074707 A1 of 07.20.2006, in which 4 planetary gears and 5 friction clutches make it possible to obtain 8 stages. Boxes of this type are quite complex and do not allow further increasing the number of steps without a significant deterioration in overall dimensions.

The second type is the so-called robotic gearboxes (patents DE 19821164 A1, 11/18/1999; DE 19944879 A1, 03/22/2001), containing, as a rule, a two-layer shaft, the external and internal parts of which are connected alternately with friction clutches to the motor shaft , providing the transmission of rotational motion through the intermediate shafts with the desired gear ratio due to the inclusion of the corresponding gear pairs. A characteristic feature of such boxes is the preliminary preparation of the corresponding stage. When the car moves and accelerates, for example, in the fourth stage (the external gearbox shaft is involved), the controlled clutch located on the intermediate shaft and responsible for the fifth stage is already engaged and, as soon as the car reaches the required speed, the control system switches friction coupling, providing separation of the motor shaft with the external shaft and its connection with the internal. The disadvantage of such boxes is the fact that the power from the motor shaft is transmitted in a single stream either through an external shaft or through an internal one. As a result, structural elements that transmit motion are loaded with a maximum moment.

To eliminate this drawback, they began to use branched kinematic schemes. They contain a mechanism that separates the input stream from the engine into two parallel branches, and a planetary mechanism that summarizes both power flows on the output shaft of the gearbox (US 6869379 B2, 03/22/2005; WO 03/025431 A1, 03/27/2003; US 7004878 B2, 02.28.2006; WO 2006/032312 A1, 03.30.2006). Such gearboxes are called dual-threaded. Along with summation, they provide single-threaded modes, which are carried out by stopping one of the links of the planetary mechanism. As a result, a significant increase in the number of steps is achieved in almost the same or even smaller overall dimensions. At the same time, a drawback of such schemes was revealed: a relatively high torque acts on controlled couplers in both single-threaded and two-threaded modes, which reduces their reliability and service life.

The proposed technical solution eliminates the indicated drawback of dual-flow gearboxes. The closest analogue of the proposed solution is the box scheme from the patent WO 2006/032312 A1, 03.30.2006.

The problem to which the invention is directed is to create a gearbox with an increased service life with a minimum number of gears and controlled couplers.

The technical result that can be obtained by carrying out the invention is that the total number of couplings and gear couplings is reduced in the gearbox scheme, and due to the rational arrangement of the planetary mechanism, the effective loads on the controlled couplings are significantly reduced.

The above technical result is achieved due to the fact that the gearbox is mainly for transport vehicles containing a fixed body, input and output links, a planetary mechanism in the form of a carrier, a sun wheel and an epicycle interacting with each other, a single and two-layer shafts, the latter consisting of external and internal shafts, controlled coupling, designed to connect the internal and external shafts, gears mounted on the shafts and forming pairs that are constantly in clinging and transmitting movement from shaft to shaft with the help of controlled couplers, providing a different gear ratio between the shafts, the following additions have been introduced: two controlled couplers for connecting the inner shaft to the fixed case and the outer shaft to the fixed case, respectively; the carrier, the sun wheel and the epicyclic of the planetary mechanism are connected respectively to the input link, to the internal and external shafts, and a single shaft is connected to the output link.

The invention is illustrated by drawings:

- figure 1 is a kinematic diagram of a patented gearbox;

- figure 2 is a diagram of the mechanisms of the gearbox transmitting the moment from the input link when operating at 1 stage;

- figure 3 is a diagram of the mechanisms of the gearbox transmitting the moment from the input link when working on 2 stages;

- figure 4 is a diagram of the mechanisms of the gearbox transmitting the moment from the input link when working at 3 stages;

- figure 5 - diagram of the mechanisms of the gearbox, transmitting the moment from the input link when working on 4 stages;

- Fig.6 is a diagram of the mechanisms of the gearbox transmitting the moment from the input link when operating at 5 steps;

- Fig.7 is a diagram of the mechanisms of the gearbox, transmitting the moment from the input link when working at 6 steps;

- Fig. 8 is a diagram of gearbox mechanisms transmitting a moment from an input link when operating at 7 steps;

- Fig.9 is a diagram of the mechanisms of the gearbox transmitting the moment from the input link when working at 8 steps;

- figure 10 is a diagram of the mechanisms of the gearbox transmitting the moment from the input link when working at 9 stages;

- 11 - diagram of the mechanisms of the gearbox, transmitting the moment from the input link when working at 10 steps;

- Fig - diagram of the mechanisms of the gearbox, transmitting the moment from the input link when working at 11 steps;

- Fig. 13 is a diagram of gearbox mechanisms transmitting a moment from an input link when operating at 12 stages;

- Fig. 14 is a diagram of gearbox mechanisms transmitting a moment from an input link when operating in the 1st reverse gear;

- Fig. 15 is a diagram of gearbox mechanisms transmitting a moment from an input link when operating in 2nd reverse gear;

The gearbox (figure 1) consists of:

- a stationary body 1 (shown by oblique hatching), input link 2 and output link 3, planetary gear 4 in the form of carrier 5 interacting with each other, sun wheel 6 and epicycle 7; carrier 5 is fixedly connected to input link 2;

- a single shaft 8 and a two-layer shaft 9, and the two-layer shaft 9 consists of an external shaft 10 and an internal shaft 11; the outer shaft 10 is fixedly connected to the epicycle 7, the inner shaft 11 is fixedly connected to the sun wheel 6, a single shaft 8 is connected to the output link 3;

- managed coupling 12, designed to connect the inner 11 and the outer 10 shafts;

- gears mounted on shafts 8, 10, 11 and forming pairs 13, 14, 15, 16, 17, constantly engaged and transmitting movement from shaft to shaft using controlled couplers 18, 19, 20, 21, 22 providing a different gear ratio between the shafts;

- two controlled coupling couplings 23 and 24 for connecting, respectively, the inner shaft 11 with the fixed housing 1 and the outer shaft 10 with the fixed housing 1.

The gearbox operates as follows:

- at the first stage (figure 2) included the clutch 12 and 19, the inner 11 and the outer 10 shafts are connected by a clutch 12. As a result, the planetary mechanism 4 is locked and rotates as a whole. Thus, the input power flow passes without changes through the input link 2, carrier 5, the sun wheel 6, the epicyclic 7, the two-layer shaft 9, the coupling 19 and the gear pair 14 to a single shaft 8, fixedly connected to the output link 3;

- at the second stage (Fig. 3), couplers 19 and 21 are turned on, the input power flow is divided into a planetary mechanism 4, part of the flow through the epicyclic 7 and the outer shaft 10 is coupled to gear pair 14 through the coupling 19, and the second part through the sun wheel 6, the inner shaft 11 and the included coupling 21 goes to the gear pair 16, the summation of the flows occurs on a single shaft 8, and the entire flow enters the output link 3;

- in the third stage (figure 4), the inner 11 and outer 10 shafts of the two-layer shaft 9 are connected by a coupling 12, the planetary mechanism 4 is locked and rotates as a whole. The input power flow passes without changes through the input link 2, carrier 5, the sun wheel 6, epicycle 7, two-layer shaft 9, the included coupling 21 and the gear pair 16 to the output link 3;

- at the fourth stage (Fig. 5), the couplers 19 and 20 are turned on, the input power flow is divided into a planetary mechanism 4, part of the flow through the epicyclic 7 and the outer shaft 10, with the help of the coupling 19, goes to the gear pair 14, the second part through the sun wheel 6, the inner shaft 11 and the included clutch 20 goes to the gear pair 15, the summation of the flows occurs on a single shaft 8, and the entire flow enters the output link 3;

- at the fifth stage (Fig.6), the inner shaft 11 and, accordingly, the sun wheel 6 of the planetary gear 4 is stopped by the coupling 23, the input stream from the link 2 through the carrier 5, the epicycle 7 and the outer shaft 10 comes to the single shaft 8 through the gear pair 14 connected to the outer shaft 10 with a coupling 19;

- at the sixth stage (Fig. 7), when the couplers 21 and 18 are turned on, the input power flow is divided into a planetary mechanism 4, a part of the flow through the epicyclic 7 and the external shaft 10 goes to the gear pair 13 with the help of the coupling 18, the second part through the sun wheel 6, the inner shaft 11 and the included coupling 21 goes to the gear pair 16, the summation of the flows occurs on a single shaft 8, motionlessly connected to the output link 3;

- at the seventh stage (Fig. 8), the couplers 12 and 18 are turned on. As a result, the planetary mechanism 4 is locked and rotates as a unit, and the input power flow passes without changes from the input link 2 through the carrier 5, the sun wheel 6, epicycle 7, a two-layer shaft 9, an included coupler 18 and a gear pair 13 to the output link 3;

- at the eighth stage (Fig. 9), when the couplers 18 and 20 are turned on, the input power flow is separated on the planetary gear 4, part of the flow through the epicyclic 7 and the outer shaft 10 through the coupler 18 goes to the gear pair 13, the second part through the sun wheel 6, the inner shaft 11 and the included coupling 20 goes to the gear pair 15, the summation of the flows occurs on a single shaft 8, motionlessly connected to the output link 3;

- at the ninth stage (Fig. 10), the couplers 12 and 20 are turned on, as a result, the planetary mechanism 4 is locked and rotates as a unit, and the input power flow passes without changes from the input link 2 through the carrier 5, the sun wheel 6, epicyclic 7, a two-layer shaft 9, an included coupler 20 and a gear pair 15 to the output link 3;

- at the tenth stage (Fig. 11), the couplers 18 and 23 are turned on. The inner shaft 11 and, accordingly, the sun wheel 6 of the planetary gear 4 are stopped, the input stream from the link 2 through the carrier 5, the epicycle 7 and the outer shaft 10 comes to the single shaft 8 through a gear pair 13 connected to the outer shaft 10 by a coupler 18;

- at the eleventh stage (Fig. 12), the couplers 24 and 21 are turned on. As a result, the outer shaft 10 and the epicycle 7 of the planetary gear 4 are stopped. The input power flow from link 2 through carrier 5, the sun wheel 6 and the inner shaft 11 comes to the output link 3 through a gear pair 16 connected to the inner shaft 11 by a coupler 21;

- at the twelfth stage (FIG. 13), the couplers 24 and 20 are turned on. The outer shaft 10 and the epicycle 7 of the planetary gear 4 are stopped. The input stream from the link 2 through the carrier 5, the sun wheel 6 and the inner shaft 11 comes to the output link 3 through the gear pair 15 connected to the inner shaft 11 by the coupling coupling 20;

- in the first reverse gear (Fig. 14), the planetary mechanism 4 is locked and rotates as a whole using the coupling 12, thus, the input power flow passes without changes from the input link 2 through carrier 5, the sun wheel 6, epicyclic 7, a two-layer shaft 9, an included clutch 22 and a gear pair 17 with a spurious wheel to the output link 3;

- in the second reverse gear (Fig. 15), the epicycle 7 of the planetary mechanism 4 is stopped by the coupling 24, the input stream from the link 2 through the carrier 5, the sun wheel 6 and the inner shaft 11 comes to the output link 3 through the gear pair 17 with a spurious wheel, connected to the inner shaft 11 by a coupler 22;

It should be noted that in the patented gearbox, in contrast to the prototype, the direction of rotation of the input link 2 does not coincide with the direction of rotation of the output link 3. Change of the direction of rotation without changing the kinematic scheme of the gearbox can be carried out by adding a gear pair in front of input link 2 or after output link 3 .

All the steps performed by the gearbox, with the respective controlled couplers included (shown by the “×” sign) are summarized in Table 1. The gear ratios of the gearbox at each stage are also shown there, and the sign in front of the gear ratio means the type of movement to be assumed: " + "- forward; "-" - back. Table 1 also shows the step of changing the gear ratio, defined as the ratio of the previous gear ratio to the next.

Table 1 Gear number Coupling states Gear ratio Gear ratio 12 eighteen 19 twenty 21 22 23 24 one × × 3.00 2 × × 2.93 1.02 3 × × 2.79 1.05 four × × 2.46 1.13 5 × × 2.05 1.20 6 × × 1.86 1.10 7 × × 1.42 1.31 8 × × 1.38 1.03 9 × × 1.29 1.07 10 × × 0.97 1.33 eleven × × 0.89 1.09 12 × × 0.41 2.17 R1 × × -3.00 R2 × × -1.00

Patented gearbox has three degrees of freedom, i.e. for its operation at each stage two controlled couplers must be included. As the analysis of Figs. one of the links 6 or 7 of the planetary mechanism stops 4. There are four such single-threaded steps - these are the steps numbered 5, 10, 11 and 12 (see table 1). The second type of single-threaded steps corresponds to the situation when both shafts 10 and 11 of the two-layer shaft 9 are connected by a coupling 12. In addition, due to the rigid connection of the shafts 10 and 11 with the links 7 and 6 of the planetary mechanism 4, the latter is blocked and rotates as a whole. The number of steps of the second type - with the blocking of the planetary mechanism - is also four; these are steps 1, 4, 7 and 9 (see table 1). If none of the couplers 23, 24 or 12 is turned on, then the box implements a dual-stream operation mode. This mode is also performed in four steps. These are steps 2, 3, 6 and 8 (see table 1).

Thus, the proposed gearbox with only four pairs of 13, 14, 15 and 16 gears can realize twelve steps: four single-threaded steps with the stop of one of the links of the planetary gear, four single-threaded steps with a planetary gear lock and four two-threaded gears, the gear ratios of which equal to the pairwise sums of the gear ratios of the first four single-threaded steps.

As you can see, the patented gearbox has the same number of steps as that selected as a prototype for the patent WO 2006/032312, 03.30.2006, but with fewer couplings and gears. The connection of the input link of the gearbox with the carrier of the planetary mechanism leads to the planetary mechanism performing a gear ratio of less than 1, therefore, controlled couplers are less loaded.

Claims (1)

The gearbox is mainly for transport vehicles, containing a fixed housing, input and output links, a planetary mechanism in the form of a carrier, a sun wheel and an epicycle interacting with each other, a single and two-layer shafts, the latter consisting of external and internal shafts, controlled by a coupler designed to connections of internal and external shafts, gears mounted on shafts and forming pairs that are constantly engaged and transmitting movement from shaft to shaft using chain couplings, providing a different gear ratio between the shafts, characterized in that the gearbox contains two controllable clutch couplings for connecting the inner shaft to the fixed housing and the outer shaft to the fixed housing, respectively; the carrier, the sun wheel and the epicyclic of the planetary mechanism are connected respectively to the input link, to the internal and external shafts, and a single shaft is connected to the output link.

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