Gear box

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

 

The invention relates to the field of engineering, namely the mechanisms of stepwise speed change, and can be used mainly in the automotive industry.

Currently, automobile gearbox improved in the direction of increasing the number of stages while striving to reduce the number of gear pairs and managed coupling couplings, and, consequently, to increase the efficiency of the box and improve its physical characteristics.

There are two types of automotive transmissions. The first type is the planetary boxes containing planetary mechanisms, the number of which determines the number of steps box. An example is transmission, is known from the patent WO 2006/074707 A1 from 20.07.2006, in which 4 of the planetary mechanism and 5 friction clutches allow you to get 8-speed transmission. Boxes of this type are quite complex and do not allow in the future to increase the number of stages without significant loss of mass and size parameters.

The second type is the so - called robotic gearbox (patents DE 19821164 A1, 18.11.1999; DE 19944879 A1, 22.03.2001)containing, as a rule, double-layered shaft, the outer and inner part of which in turn through a friction clutch connected to the motor shaft, ensuring the transmission of rotational motion through intermediate shafts with the desired lane is contributed by the respect due to the inclusion of the respective gear pairs. A characteristic feature of these boxes is a preliminary preparation of the corresponding level. When the car is moving and accelerating, for example, at the fourth stage (using external shaft gear)driven coupling coupling located on the intermediate shaft and is responsible for the fifth step, already included and, as soon as the vehicle reaches the desired speed, the control system switches the friction coupling, providing separation of the motor shaft with the outer shaft and connect it to an internal. The drawback of such boxes is the fact that the power from the motor shaft is transmitted by a single thread through the external shaft, or through the internal. As a result, the structural elements that transmit the movement of the loaded maximum torque.

To address this shortcoming began to apply branched kinematic scheme. They contain a mechanism that separates the input stream from the engine into two parallel branches, and the planetary mechanism, summarizing both power flow on the output shaft of the gearbox (US 6869379 B2, 22.03.2005; WO 03/025431 A1, 27.03.2003; US 7004878 B2, 28.02.2006; WO 2006/032312 A1, 30.03.2006). Such transmission is called a double-flow. Along with summation they provide and single-threaded modes that are stopping one of the links of the planetary mechanism. In achiev is Tate achieved a substantial increase in the number of stages in almost the same or even smaller dimensions. At the same time revealed and the disadvantage of these schemes: controlled coupling coupling on single-threaded and dual stream modes is relatively high torque, which reduces their reliability and service life.

The proposed solution allows to eliminate the above drawback dual stream transmissions. The closest analogue of the proposed solution is a diagram of the box from the patent WO 2006/032312 A1, 30.03.2006.

The task, which is aimed by the invention is the creation of a gearbox with a high service life with a minimum number of the gears and driven coupling sleeves.

The technical result, which can be obtained by carrying out the invention, is that in the scheme of transmission reduced the total number of coupling clutches and the gears, but due to the rational arrangement of the planetary mechanism is substantially reduced current load on the driven coupling clutch.

The above technical result is achieved due to the fact that the gearbox is mainly for vehicles, comprising a fixed housing, input and output units, planetary gear mechanism in the form of interacting carrier, sun gear and epicycle, single-and double shafts, the latter consists of nesnera and inner shafts, managed coupling coupling, intended to connect the inner and outer shafts, gears mounted on the shafts and forming a pair, are constantly in mesh and transmit motion from the shaft to the shaft by means of controlled coupling couplings, providing different gear ratio between the shafts, put the following additions: two controlled coupling clutch for connecting respectively the inner shaft with a fixed housing and an outer shaft with a fixed housing; carrier, a sun wheel and apical planetary mechanism connected respectively with the input element, with the inner and outer shafts, and a single shaft connected to the output link.

The invention is illustrated in the drawings:

- figure 1 is a kinematic diagram of the patent-pending gearbox;

- figure 2 - scheme of the mechanisms of transmission, the transmitting torque from the input element when working on level 1;

- figure 3 - scheme of the mechanisms of transmission, the transmitting torque from the input element when working on 2 stages;

- figure 4 - scheme of the mechanisms of transmission, the transmitting torque from the input element when working on 3 stages;

- figure 5 - scheme of the mechanisms of transmission, the transmitting torque from the input element when working in 4 steps;

- 6 - scheme of the mechanisms of transmission, the transmitting torque from the input element when working on 5 stages;

- f is g - the scheme of the mechanisms of transmission, the transmitting torque from the input element when working on 6 stages;

- pig diagram of the mechanisms of transmission, the transmitting torque from the input element when working on 7 stages;

- figure 9 - diagram of the mechanisms of transmission, the transmitting torque from the input element when working in 8 steps;

- figure 10 - diagram of the mechanisms of transmission, the transmitting torque from the input element when working in 9 steps;

- 11 - diagram of the mechanisms of transmission, the transmitting torque from the input element when working on 10 stages;

- pig diagram of the mechanisms of transmission, the transmitting torque from the input section during the work on the 11th;

- pig diagram of the mechanisms of transmission, the transmitting torque from the input element when working on the 12 steps of;

- pig diagram of the mechanisms of transmission, the transmitting torque from the input element when working on the 1st reverse gear;

- pig diagram of the mechanisms of transmission, the transmitting torque from the input element when working on the 2nd reverse gear;

Transmission (figure 1) consists of:

- fixed housing 1 (shown by oblique hatching), an input link 2 and output link 3, planetary gear mechanism 4 in the form of interacting drove 5, the sun gear 6 and epicycle 7; drove 5 still connected with the input link 2;

single shaft 8 and the two-layer shaft 9, being the m double-layered shaft 9 consists of an outer shaft 10 and the inner shaft 11; the outer shaft 10 is stationary connected with epicycles 7, the inner shaft 11 is stationary connected with a sun wheel 6, single shaft 8 to the output link 3;

- managed coupling coupling 12, which is designed for connection of the inner 11 and outer shaft 10;

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

- managed two coupling sleeves 23 and 24 for connection, respectively, the inner shaft 11 with the stationary housing 1 and the outer shaft 10 with a fixed housing 1.

Running transmission as follows:

- at the first stage (figure 2) enabled hitch coupler 12 and 19, the inner 11 and outer shafts 10 are connected clutch coupling 12. In the planetary gear mechanism 4 is locked and rotates as a single unit. Thus, the input power flux unchanged passes through the input link 2, carrier 5, a sun wheel 6, apill 7, double-layered shaft 9, the coupling sleeve 19 and the gear pair 14 to the single shaft 8 fixedly connected with the output element 3;

- on the second level (3) enabled hitch coupling 19 and 21, the input power flow is divided into a planetary mechanism 4, a part of the flow through epicycle 7 and the outer shaft 10 with p the power coupling clutch 19 is a gear pair 14, the second part is through the sun wheel 6, the inner shaft 11 and included coupling the coupling 21 is a gear pair 16, the summation of the flows occurs on a single shaft 8, and the entire flow arrives at the output link 3;

- the third stage (figure 4) inner 11 and outer shafts 10 double-layered shaft 9 is connected by coupling clutch 12, the planetary gear 4 is locked and rotates as a single unit. The input power flux unchanged passes through the input link 2, carrier 5, a sun wheel 6, apill 7, double-layered shaft 9 included coupling the coupling 21 and the gear pair 16 to the output link 3;

- fourth step (5) includes coupling the coupling 19 and 20, the input power flow is divided into a planetary mechanism 4, a part of the flow through epicycle 7 and the outer shaft 10 by means of coupling of the coupling 19 is a gear pair 14, the second part is through the sun wheel 6, the inner shaft 11 and included the clutch 20 is a gear pair 15, the summation of the flows occurs on a single shaft 8, and the entire flow arrives at the output link 3;

- at the fifth stage (6) of the inner shaft 11 and consequently the sun wheel 6 of the planetary mechanism 4 is stopped by the clutch 23, the input stream from level 2 through the carrier 5, apill 7 and the outer shaft 10 comes on a single shaft 8 through a gear pair 14, is connected to the external shaft 10 clutch coupling 19;

- in the sixth level (Fig.7) when introducing the different coupling sleeves 21 and 18 input power is divided into planetary mechanism 4, part of the flow through epicycle 7 and the outer shaft 10 by means of coupling coupling 18 is a gear pair 13, the second part is through the sun wheel 6, the inner shaft 11 and included coupling the coupling 21 is a gear pair 16, the summation of the flows occurs on a single shaft 8 fixedly connected with the output element 3;

at the seventh stage (Fig) enabled hitch coupler 12 and 18. In the planetary gear mechanism 4 is locked and rotates as a unit, and the input power flux unchanged passes from the input element 2 through the carrier 5, a sun wheel 6, apill 7, double-layered shaft 9, included the coupling sleeve 18 and the gear pair 13 to the output link 3;

on the eighth stage (Fig.9) when the coupling sleeves 18 and 20 input power is divided into planetary mechanism 4, a part of the flow through epicycle 7 and the outer shaft 10 by means of coupling coupling 18 is a gear pair 13, the second part is through the sun wheel 6, the inner shaft 11 and the included hitch coupler 20 is a gear pair 15, the summation of the flows occurs on a single shaft 8 fixedly connected with the output element 3;

ninth stage (figure 10) enabled hitch coupler 12 and 20, the planetary gear 4 is locked and rotates as a unit, and the input power flux unchanged passes from the input element 2 through the carrier 5, a sun wheel 6, apill 7,double-layered shaft 9, included coupling sleeve 20 and the gear pair 15 to the output link 3;

- in the tenth step (11) includes coupling coupling 18 and 23. The inner shaft 11 and consequently the sun wheel 6 of the planetary mechanism 4 is stopped, the input stream from level 2 through the carrier 5, apill 7 and the outer shaft 10 comes on a single shaft 8 through a gear pair 13, is connected to the external shaft 10 clutch coupling 18;

on the eleventh stage (Fig) enabled hitch coupling 24 and 21. In the stopped external shaft 10 and consequently epicycle 7 planetary mechanism 4. The input stream of power from level 2 through the carrier 5, a sun wheel 6 and the inner shaft 11 comes on the output link 3 via the gear pair 16, connected to the inner shaft 11 clutch coupling 21;

- the twelfth step (Fig) enabled hitch coupling 24 and 20. The outer shaft 10 and epicycle 7 planetary mechanism 4 is stopped. The input stream from level 2 through the carrier 5, a sun wheel 6 and the inner shaft 11 comes on the output link 3 via the gear pair 15, connected to the inner shaft 11 clutch coupling 20;

- on the first reverse gear (Fig) planetary gear mechanism 4 through the coupling of the coupling 12 is locked and rotates as a single unit, thus, the input power flux unchanged passes from the input element 2 through the carrier 5, a sun wheel 6, apill 7, double-layered shaft 9, on the Chennai clutch 22 and the gear pair 17 with an idle wheel to the output link 3;

- on the second reverse gear (Fig) epicycle 7 planetary mechanism 4 is stopped clutch coupling 24, the input stream from level 2 through the carrier 5, a sun wheel 6 and the inner shaft 11 comes on the output link 3 via the gear pair 17, parasite wheel connected to the inner shaft 11 clutch coupling 22;

It should be noted that in the patent-pending gearbox unlike the prototype of the direction of rotation of the input link 2 does not coincide with the direction of rotation of the output element 3. Changing the direction of rotation without changing the kinematic scheme of a transmission can be carried out by adding a gear pair of front link 2 or after output link 3.

All steps performed by the transmission, with the corresponding enabled controllable coupling sleeves (shown by "") are summarized in table 1. As an example, there is given gear ratio box on each level, and the sign before the value of the ratio indicates the type of the intended movement: "+" - forward; "-" to the back. Table 1 also shows the step change of gear ratio, defined as the ratio of the previous gear ratio to the next.

12
Table 1
The number before the Chi State controlled clutchesGear ratioStep gear ratio
1218192021222324
13.00
22.931.02
3 2.791.05
42.461.13
52.051.20
61.861.10
7 1.421.31
81.381.03
91.291.07
100.971.33
110.891.09
0.412.17
R1-3.00
R2-1.00

Patent-pending gearbox has three degrees of freedom, i.e. for its work at each stage should be included two controlled coupling clutch. As the analysis shows figure 2-13, gearbox when driving forward has two types of single-threaded modes: the first type corresponds to the situation when one of the shafts 10 and 11 double-layered shaft 9 is stopped by coupling clutch 23 or clutch coupling 24. P and this automatically due to the fixed connection stops one of the links 6 or 7 of the planetary mechanism 4. Such single-threaded speed manual four-speed numbers 5, 10, 11 and 12 (see table 1). The second type of single-threaded speed corresponds to the situation when both shafts 10 and 11 double-layered shaft 9 is connected clutch coupling 12. This is also due to the rigid connection of shafts 10 and 11 with parts 7 and 6 of the planetary gear 4, the latter is locked and rotates as a single unit. The number of stages of the second type with locking planetary gear - four; this stage under the numbers 1, 4, 7 and 9 (see table 1). If not enabled, none of the hitch couplings 23, 24, or 12, box implements a two-stream mode. This mode is also on four stages. This stage under the numbers 2, 3, 6 and 8 (see table 1).

Thus, the proposed transmission with only four pairs 13, 14, 15 and 16 gears can implement the twelve steps of: four single-threaded steps to stop one of the links of the planetary mechanism, four single-threaded speed transmission with lock planetary mechanism and four double-flow speed, gear ratio which is equal pairwise sums of ratios of the first four single-threaded speed.

As you can see, patent-pending gearbox has the same number of stages as selected as a prototype for the patent WO 2006/032312, 30.03.2006, but with a smaller number of clutches and gears Connecting the input element of the gearbox with the planet carrier of the planetary mechanism performs the planetary gear reduction ratios, smaller 1, therefore, controlled coupling of the coupling is less loaded.

Transmission primarily for vehicles, comprising a fixed housing, input and output units, planetary gear mechanism in the form of interacting carrier, sun gear and epicycle, single-and double shafts, the latter consists of the external and internal shafts driven coupling coupling, intended to connect the inner and outer shafts, gears mounted on the shafts and forming a pair, are constantly in mesh and transmit motion from the shaft to the shaft by means of controlled coupling couplings, providing different gear ratio between the shafts, characterized in that the transmission contains two controlled coupling couplings for connecting respectively the inner shaft with a fixed housing and an outer shaft with a fixed housing; carrier, a sun wheel and apical planetary mechanism connected respectively with the input element, with the inner and outer shafts, and a single shaft connected to the output link.



 

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2 dwg

FIELD: mechanical engineering.

SUBSTANCE: continuously variable transmission comprises housing, input and output shafts, reverse mechanism and multi-disk planet variator provided with planet reduction gear, which define a variator. The solar pinion of the reduction gear is fit on the output shaft with interference and its epicycle is secured to the housing of the transmission. The variator has epicycle mounted in the housing of the transmission and made of a stack of disks and solar pinion made of a disk stack mounted on the output shaft of the variator connected with the output shaft of the reverse mechanism. The carrier of the variator is connected with the carrier of the planet reduction gear and consists of two disks interconnected by means of tension bolts. The disks of the carrier have shaped slots the number of which is equal to the number of axles mounted in the shaped slots for permitting change of position and interaction with the disks of the solar pinion and epicycle. The gear ration controller is build in the carrier of the variator. The planet reduction gear, planet multi-disk variator, and reverse mechanism are axially aligned.

EFFECT: prolonged service life and expanded functional capabilities.

18 cl, 8 dwg

FIELD: mechanical engineering.

SUBSTANCE: planet friction variator comprises shaft (1), solar wheel (2), corona wheel (6), carrier (4) with satellites (3), and secondary shaft (5). Corona wheel (6) that is used as a control member is connected with variator housing (11) and primary shaft (1) through friction mechanisms. Secondary shaft (5) is made in block with carrier (4) for permitting control of velocity and direction of rotation of the corona wheel by means of friction mechanisms and control electric motor (9) connected with the corona wheel.

EFFECT: simplified structure, reduced sizes, and enhanced reliability.

1 dwg

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