Rotary movement transfer mechanism

FIELD: machine building.

SUBSTANCE: rotary movement transfer mechanism includes a housing, in which an eccentric drive shaft, a driven shaft and intermediate link located on the drive shaft are installed with possibility of being rotated. The mechanism housing is provided with a central gear with satellites and free-wheel mechanisms with inlet and outlet links. Central gear is rigidly attached to the intermediate link. The inlet link of each free-wheel mechanism is connected to the corresponding satellite, and the outlet link of each free-wheel mechanism is connected to a hinge installed on the mechanism housing. Rotary movement is transferred to the outlet shaft through kinematic connection to the intermediate link.

EFFECT: improving reliability and durability of rotary movement transfer mechanism and increasing the mechanism efficiency.

8 cl, 5 dwg

 

The technical field

The invention relates to the field of mechanical engineering and the mechanism of transmission of rotational motion (gearboxes, variators), capable of changing a gear ratio.

Prior art

The known device the transmission of rotational motion [1] (gear multi-adjustable)made in the form of a manual change-speed gearboxes (CAT), where the change gear ratio occurs by breaking the flow of power through redistribution of effort between different pairs of gears due to the axial movement of Cam or splined couplings.

The disadvantages of such devices is the low reliability and durability due to small resource of these couplings, and is not large enough capacity that is capable of transmitting device, which is caused by insufficient strength of the coupling, and this deficiency particularly affects it is in the process of changing gear ratios (during shift).

Closest to the proposed invention is a device for transmitting rotational movement known as impulsive variable [2]. Here, the rotational movement is rigidly connected with the driven shaft of the Central gear is transmitted through the satellites and through the mechanisms of a free motion, the cat is who is operating in the mode of forced oscillations of the torsion the change in the amplitude of these oscillations allows you to change the gear ratio.

The disadvantages of the prototype the following:

Impulsive variator has a small reliability and durability, because in the process of transmission in the mode of forced oscillations occur continuously pulsed overload in the mechanisms of free running and the gears, which limits the lifetime of their work. In addition, the power transmitted by this variator is limited as to increase the power necessary to increase the speed of the driven shaft by increasing the amplitude of oscillation, which pulse overload only increase, resulting in accelerated destruction of the mechanisms of free running and gear teeth in contact, this will inevitably increase in power consumption, resulting in loss of efficiency impulsive variable.

Disclosure of inventions

Thus, the present invention is a mechanism for transmitting rotational motion, which would be absent the disadvantages indicated above.

The technical result is to increase the reliability and durability of the transmission mechanism of rotational motion, increasing the efficiency of the mechanism.

This technical result is achieved through the mechanism of transmission of rotational motion, which sod is rgit case, in which is installed with the possibility of rotation of the eccentric drive shaft and a driven shaft mounted on the eccentric drive shaft for rotation intermediate, this mechanism includes the mechanisms of a free motion with input and output units, the Central gear and in meshing satellites, and the Central gear rigidly connected with the intermediate link, and the input level of each free-wheeling mechanism is connected with the corresponding satellite, and the output link of each free-wheeling mechanism kinematically connected with the hinge mounted on the body of the mechanism, the rotational movement to the output shaft is transmitted via a kinematic connection with the intermediate link.

Preferred options and improved mechanism for transmitting rotational motion in accordance with the present invention are given in the dependent claims.

In accordance with other variations of the present invention at the intermediate level are annular grooves interact with arcuate guides, United housings satellites.

In accordance with the variants of the invention, the mechanism further comprises a Cam control mechanism mounted on the drive shaft. When this Cam is echanism management includes articulated traction control and a slider control.

In accordance with other variations of the present invention each satellite is installed in the housing, which kinematically connects the output link of each freewheel mechanism with hinge mounted on the body of the mechanism. Mentioned kinematic connection can be made in the form of thrust.

In accordance with the following preferred variant of the present invention kinematic connection between the output shaft is made in the form of the propeller shaft.

In accordance with another variant of the present invention the distance between the axis of rotation of the intermediate link and the center of the hinge mounted on the housing of the mechanism, (RP) is less than the radius of dividing the circumference of the Central gear (RWith), and between the values of RPand RWithit must be done in the following ratio: 0,2·RWith<RP<RWith.

Brief description of drawings

The present invention is illustrated by drawings, where:

in figure 1, figure 2 shows the kinematic diagram of the mechanism of transmission of rotational motion;

figure 3 shows a General view of the mechanism;

figure 4 shows the section a-a in figure 3;

figure 5 shows a section b-B figure 3.

The best option of carrying out the invention

The mechanism of transmission of rotational motion (see figure 1, 2, 3, 4) includes a fixed housing 1, in which oterom rotatably mounted eccentric drive shaft 2, where is the slider control 3 connected articulated traction control 4 with the slider Cam mechanism 5. On the eccentric drive shaft 2 mounted for rotation intermediate 7, United with the drive shaft 8 with the driven shaft 9. At the intermediate level are annular grooves 10, interact with the arcuate sliding blocks 11, United housings satellites 12, with each body satellites are connected by two arcuate slider. In each case the satellite is mounted for turning satellite 13, which is bonded to the Central gear 14 rigidly connected to the intermediate link. Each satellite is connected to the input element of the free wheel mechanism 15, the output element of the free wheel mechanism 16 is connected to the housing of the satellite 12, in each case the satellite is the hinge 17, which is connected with the hinge 18 thrust with one of the case hinges 19, each of which is rigidly connected to the housing 1.

Hereinafter will be described the operation of the mechanism, it should be noted that the kinematic connection of the output link of the mechanism of free running with the hinge mounted on the body of the mechanism is shown in the example in which the specified kinematically connection consists of a body of the satellite, to the m are the satellite and the mechanism of a free stroke, rod connecting the housing via a hinge mounted on the body of the mechanism. The kinematic connection of the intermediate shaft with the output shaft will be shown on the example of the propeller shaft. The above examples are not only to perform, and thus, the kinematic connection may include any other elements.

The mechanism works as follows.

Eccentric drive shaft 2, turning counterclockwise with angular velocity ω, transmits rotary motion to the intermediate link 7, this is located on the axis of this link point M describes a circle of radius e around located on the axis of the eccentric drive shaft point O. the Value of e, which is the distance between the axes of rotation of the eccentric drive shaft 2 and the intermediate part 7, we'll call the eccentricity of the mechanism. The value of e can be changed by axial movement of the slide control 3 Cam control mechanism 5. The distance between the point M and the hinges 19, mounted on the chassis of the mechanism, is constantly changing. Let this point closest to point M situated Cabinet hinge K1connected pivotally thrust with 18 located on the body of the satellite 12 by a hinge 17, the center of which is located at the point P. Since the intermediate 7 tries with point M the Central gear 14 to move to the left, it brings the body of the satellite 12, located above the point M, which hinge rod 18 [PK1] feels the force of the tension, however, because of the interaction is located in the housing 12 of the satellite gear 13 with the Central gear 14 of the input element of the free wheel mechanism 15 located in the body of the satellite 12, and begins to interact with the output link 16 and is blocked, causing the instantaneous center of velocities intermediate link is at the point P, and the mutual movement of the satellite 13, located on the ray [Ω], and the Central gear 14 simultaneously stops mutual spinning teeth in this pair of gears does not occur. For a short period of time, the body of the satellite 12 together with the locked freewheel mechanism 15 and 16, the satellite 13, the Central gear 14 and the intermediate part 7 is formed together simultaneously a single link, the distance between any two points is within a specified period of time remain constant. Thus rotation of the Central gear 14 with the other elements of the specified element relative to the housing 1 is carried out taking into account the turning of the hinges 17 and 19 of the hinge 18 thrust [PK1]. The remaining section of the satellites 12 can freely turn relative to the intermediate part 7 hour against the howl of the arrow, without causing locking of the respective mechanisms of free running, along with corresponding hinge 18 thrust will feel the efforts compression.

As further turning of the driven shaft around the point O (figure 2-4 corresponds to the turning of the beam [Ω]) is closest to point M will be powered hinge 19, the associated articulated thrust 18 with the nearest (in the direction of motion of a point M) housing the satellite 12, and now in this case the satellite 12 will occur simultaneously locking freewheel mechanism 15 and 16, after which the mechanism of a free motion of the body of the satellite associated with the hinge 18 thrust [PK1], is unlocked. The more the number of blocks of satellites 12, the smoother will work mechanism, because uniformity is caused by the processes lock and unlock mechanisms freewheel 15 and 16 corps of satellites 12, at the same time simultaneously blocked only one mechanism of free running, and all other mechanisms of free running are unlocked, allowing the respective housings of the satellites 12 to rotate relative to the Central gear 14 in a clockwise direction. The process of locking and unlocking mechanisms of the free motion is entirely due to the spatial location of the point M, which changes when p is borciani eccentric drive shaft 2. Rotational movement of the intermediate part 7 is transmitted via the propeller shaft 8 on the driven shaft 9. In this case, transmission of rotational motion to a driven shaft 9 may be implemented by means of hinges of equal angular speeds, rocker mechanism.

Thus, rotational movement of the intermediate element 7 together with the Central gear 14 corresponds to a rotation of a circle of radius RPwhere R is the center of the hinge mounted on the housing of the mechanism, with the center point M, which rolls without slipping in the middle of a fixed circle of radius (RP+e) with center at point O, while the instantaneous center of velocities of intermediate 7 every time will be located in the hinge 17 of the body of the satellite 12, which will be on the ray [OHM]. If we denote the ratio (RP/RWith) as kp(that is, kp=RP/RWith), where kpis the reduction coefficient, a RWithis the radius of dividing the circumference of the Central gear, the gear ratio i of the proposed gear will be as follows: i=(RWith·kp+e)/e. Specified gear ratio withdrawn by the applicant after the experimental research.

We see that in fact the pole gearing the proposed mechanism will be in pole gear Central pole is neither 14 with satellite 13, which is located at a distance of RWithfrom the point O, and is much closer to the point O, that is, at the point P, which is at a distance of RPfrom the point O.

As already mentioned, the transmission in the proposed mechanism occurs simultaneously through the locked freewheel mechanism and in the complete absence of mutual run-in teeth of the Central gear 14 and loaded the satellite 13, which reduces power consumption and minimizes the load of the main transmission elements of the mechanism, resulting in increased efficiency of the proposed mechanism and increases its reliability and durability.

Sources of information

1. Kharitonov S.A. Automatic transmission. Year: Astrel - ACT, 2003, 479 S.

2. Maltsev SCI Impulsive variable-speed drives. M: motor cycle", 1963, 278 S.

1. The mechanism of transmission of rotational motion, comprising a housing in which is installed with the possibility of rotation of the eccentric drive shaft and a driven shaft mounted on the eccentric drive shaft for rotation intermediate, this mechanism includes the mechanisms of a free motion with input and output units, the Central gear and in meshing satellites, wherein the Central gear is rigidly connected with the intermediate link, the input level of each free wheel mechanism connected to suitable the existing satellite, and the output link of each free-wheeling mechanism kinematically connected with the hinge mounted on the body of the mechanism, the rotational movement to the output shaft is transmitted via a kinematic connection with the intermediate link.

2. The mechanism of transmission of rotational motion according to claim 1, characterized in that it further comprises a Cam control mechanism mounted on the control shaft.

3. The mechanism of transmission of rotational motion according to claim 2, characterized in that the Cam control mechanism includes an articulated traction and slide control.

4. The mechanism of transmission of rotational motion according to claim 1, characterized in that the output link of each mechanism of a free course through the body of the satellite is connected kinematically with the hinge mounted on the body.

5. The mechanism of transmission of the rotational movement according to claim 4, characterized in that the kinematic connection of the casing via a hinge mounted on the body of the mechanism, made in the form of thrust.

6. The mechanism of transmission of the rotational movement according to claim 4, characterized in that the intermediate element are annular grooves interact with arcuate guides, United housings satellites.

7. The mechanism of transmission of rotational motion according to claim 1, characterized in that the kinematic relationship premiato the tion of the shaft with the output shaft is made in the form of a cardan shaft, either in the form of hinges of equal angular speeds, either in the form of a rocker mechanism.

8. The mechanism of transmission of rotational motion according to claim 1, characterized in that the distance between the axis of rotation of the intermediate link and the center of the hinge mounted on the body mechanism (RP), is less than the radius of dividing the circumference of the Central gear (RWith), and between the values of RPand RWithit must be done in the following ratio: 0,2·RWith<RP<RWith.



 

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