RU2500938C1 - Converter of rotational movement to translational movement - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: movement converter includes a housing, in which there coaxially installed are inlet and outlet shafts, a central gear wheel rigidly fixed on the housing coaxially to the inlet shaft. On the outlet shaft there installed are two similar elliptical gear wheels of one and the same size, which are turned relative to each other through 180°, and two identical satellites spaced at an angle of 180°. Each satellite consists of a cylindrical gear and an elliptical gear, which are connected to each other by means of the shaft, as well as a carrier fixed on the inlet shaft. A central fixed gear wheel is externally engaged with cylindrical gears of both satellites. Each elliptical gear wheel of the outlet shaft is engaged with one of elliptical gears of satellites. Elliptical gears of satellites and elliptical gear wheels of the outlet shaft are installed on their shafts so that shaft rotation axis passes through a point called a dividing ellipse focus of the elliptical gear wheel of the outlet shaft or elliptical gear of the satellite, which is located on large semi-axis of the dividing ellipse at distance c from the dividing ellipse centre.

EFFECT: increasing operational life and improving mechanism compactness.

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Description

The invention relates to the field of engineering, and in particular to mechanisms for converting rotational motion into reciprocating and vice versa.

There are a fairly large number of mechanisms for converting rotational motion into reciprocating, but mechanisms with elliptical gears have not yet been widely used among them. Therefore, the following mechanisms can be attributed to analogues.

The well-known articulated four-link consisting of a crank connected by a rotational kinematic pair with a connecting rod, which, in turn, is connected to the beam using a rotary kinematic pair. (Smelyagin A.I. Structure of mechanisms and machines: Textbook. - M.: Higher School, 2006. - 304 p., P. 89, Fig. 2.31).

The main disadvantages of the articulated four link, with its relative simplicity, are the relatively large dimensions and low volume utilization.

A well-known rocker mechanism, consisting of a crank, with a stone (slider) fixed on it in a rotational kinematic pair and a rocker connecting through a rotational kinematic pair with a body and through a translational kinematic pair with a stone. (Smelyagin A.I. Structure of mechanisms and machines: Textbook. - M.: Higher School, 2006. - 304 p., P. 89, Fig. 2.32).

This design also has a number of drawbacks, it is distinguished by its relatively large dimensions and low volume utilization coefficient, as well as the presence of a translational kinematic pair transmitting a significant load, which tends to wear out quickly, which sharply reduces the resource of the mechanism.

A known mechanism for transmitting movement, which includes a housing, an input shaft on thrust bearings, a converter for oscillating motion of the input shaft into rotational motion of the output shaft, an output shaft on thrust bearings and equipped with a flywheel, characterized in that the transmission mechanism of the movement is made in two stages, the first stage comprising input gear wheel and two identical gears engaged with it, equipped with crank fingers and located symmetrically with respect to the vertical axis rotation of the input shaft, and the second stage includes the gear of the output shaft and two identical gears engaged with it, equipped with crank fingers and located symmetrically with respect to the vertical axis of rotation of the output shaft, with the crank fingers of the first and second stages pairwise connected by rocker arms. (RF patent No. 2239739, F16H 21/40, F01C 9/00).

The design of this mechanism of transmission of motion allows you to use it also for converting rotational motion into reciprocating. However, the study of its structure shows that it is based on two parallel mounted articulated four-link chains (smaller gears with fingers - cranks, rocker arms - connecting rods, large gears with fingers - rocker arms) to which additional links are attached, while the reverse-rotational movement in this mechanism is provided precisely due to the articulated four-link, the disadvantages of which have already been shown above. Another important feature of this mechanism is the presence of a significant radial load and bending moments in most rotational kinematic pairs due to the fact that almost all links are fixed cantilever, which leads to an increase in the size and complexity of bearing assemblies and, as a result, an increase in the cost of the entire mechanism.

Known rocker-link mechanism, including a leading link containing a crank made in the form of a disk mounted with the possibility of rotation around the axis with an eccentrically mounted finger, a driven link comprising two parallel guides forming a link mounted between two supports with the possibility of interaction with the finger, characterized in that the guide wings are cylindrical, of the same diameter and connected to the supports by a connecting element, the axis of which is parallel to the axes of the guides, is mounted to rotate around the axis of the connecting element, and the contour of the cross section of the finger is given by the equations

$$x\left(p\right)=-\frac{p}{2}\left[\frac{\mathrm{<figure-callout\; id="2"\; label="l\; cos"\; filenames="00000006.png,00000008.png"\; state="\{\{state\}\}">l\; </figure-callout>}}{\sqrt{{\cos }^{}}}-\frac{2r}{\sqrt{\mathrm{one}+p^2}}\right],$$

$$y\left(p\right)=-\frac{\mathrm{one}}{2}\left[\frac{\mathrm{<figure-callout\; id="2"\; label="l\; cos"\; filenames="00000006.png,00000008.png"\; state="\{\{state\}\}">l\; </figure-callout>}{\cos }^{}{}^2{\phi }_{\mathrm{<figure-callout\; id="2"\; label="max\; cos"\; filenames="00000006.png,00000008.png"\; state="\{\{state\}\}">max\; </figure-callout>}}}{\sqrt{{\cos }^{}}}-\frac{2r}{\sqrt{\mathrm{one}+p^2}}\right],$$

Hsinφ _max = L,

where φ _max - the maximum angle of rotation of the wings around the connecting element;

l is the distance between the axes of the guiding wings;

r is the radius of the guide wings;

H is the swing radius of the wings;

L is the radius of rotation of the finger;

x is the abscissa axis for the function that defines the contour of the cross section of the finger;

y is the ordinate axis for the function defining the contour of the cross section of the finger;

p is the parameter of the function, and p y '(x),

a - the width of the groove in the wings is equal to the maximum diameter of the finger (RF patent No. 2091641, F16H 21/40).

In the rocker-lever mechanism there is a higher kinematic pair with a point touch between the finger and the guides, which makes it impossible to use this mechanism to transfer medium and significant forces due to extremely high contact stresses and as a result of the rapid wear of such a kinematic pair.

In the rocker-lever mechanism there is a higher kinematic pair with a point touch between the finger and the guides, which makes it impossible to use this mechanism to transfer medium and significant forces due to extremely high contact stresses and as a result of the rapid wear of such a kinematic pair.

Thus, the task is to create a converter of rotational motion into a rotational-rotational motion on a fundamentally different principle of obtaining a rotational-rotational motion.

The technical result is a mechanism characterized by compactness and at the same time the possibility of transmitting significant effort and a significant expected service life, as well as the possibility of simple dynamic balancing and the almost complete absence of radial loads and bending moments on the input and output shafts.

The technical result is solved by a device comprising a housing in which the input and output shafts are coaxially mounted, a central stationary gear wheel fixedly mounted on the housing coaxially with the input shaft, two identical elliptical gears of the same size and rotated 180 ° relative to each other are installed on the output shaft, two identical satellites, spaced 180 ° apart, each satellite consists of a cylindrical gear and an elliptical gear connected by a shaft, a carrier mounted on the input shaft moreover, the shafts of both satellites are fixed at the ends of the carrier in rotary kinematic pairs, the central stationary gear wheel is in external engagement with the cylindrical gears of both satellites, and each elliptical gear wheel of the output shaft is engaged with one of the elliptical gears of the satellites, in addition, cylindrical gears the satellites and the central fixed gear are made with the same diameters, and both elliptical gears are made the same size as the elliptical they are the gears of the satellites, in addition, the elliptical gears of the satellites and the elliptical gears of the output shaft are mounted on their shafts so that the axis of rotation of the shaft passes through a point called the focus of the dividing ellipse of the elliptical gear of the output shaft or the elliptical gear of the satellite, which is located on the major axis of the dividing ellipse at a distance from the center of the dividing ellipse

$$c=\sqrt{a^2-{\mathrm{<figure-callout\; id="2"\; label="b"\; filenames="00000006.png,00000008.png"\; state="\{\{state\}\}">b</figure-callout>}}^2},$$

where a and b are the major and minor axis of the dividing ellipse, respectively,

thus, the continuity of their engagement is achieved.

The technical result is achieved due to the fact that the mechanism uses only gearing and rotational kinematic pairs, which are distinguished by a long service life, a wide range of transmitted forces and high compactness, as well as the fact that in this mechanism all links except the output rotate at a constant speed, as a result what they can be easily balanced, in addition, the use of two satellites instead of one, although it complicates the design, but reduces dimensions due to the load sharing between the satellite E and allows practically total elimination of radial loads and bending moments at the input and output shafts, which also simplifies the design and reduces the dimensions of the respective elements.

The invention is shown in the drawings.

Figure 1 is a structural diagram of a Converter for rotational motion in the reciprocating.

Figure 2 - view And without the housing.

Figure 3 - view B without housing.

The rotary-to-rotary motion converter comprises a housing 1 in which input 2 and output 3 shafts are coaxially mounted, a central fixed gear 4 fixedly mounted on the housing 1 coaxially with input shaft 2. Two identical elliptical gears 5 and 5 are mounted on the output shaft 3 6 of the same size, rotated 180 ° relative to each other, two identical satellites spaced 180 ° apart, each satellite consists of a spur gear 7 and 8 and an elliptical gear 9 and 10 interconnected by a shaft 11 and 12, carrier 13, mounted on the input shaft, and at the ends of the carrier in rotational kinematic pairs, the shafts 11 and 12 of both satellites are fixed, the central fixed gear 4 is in external engagement with the spur gears 7 and 8 of the satellites, and each elliptical gear 5 and 6 of the output shaft is engaged with one of the elliptical gears of the satellites 9 and 10. In addition, the spur gears 7 and 8 of the satellites and the central stationary gear 4 are made with the same diameters, and both are elliptical Sgiach output shaft gears 5 and 6 are of the same size with elliptical gears 9 and 10 satellites. In addition, the elliptical gears of the satellites 9 and 10 and the elliptical gears 5 and 7 of the output shaft are mounted on their shafts in such a way that the axis of rotation of the shaft passes through a point called the focus of the dividing ellipse of the elliptical gear wheel of the output shaft or the elliptical gear of the satellite, which is located on a large semi-axes of the dividing ellipse at a distance c from the center of the dividing ellipse

$$c=\sqrt{a^2-{\mathrm{<figure-callout\; id="2"\; label="b"\; filenames="00000006.png,00000008.png"\; state="\{\{state\}\}">b</figure-callout>}}^2},$$

where a and b are the major and minor semiaxis of the dividing ellipse, respectively. Thus, the continuity of their engagement is achieved.

The mechanism works as follows.

The input shaft 2 is communicated with a rotational movement, which is transmitted to the carrier 13, due to this, the cylindrical gears of the satellite 7 and 8 are driven around the stationary central gear 2, the rotational movement of the cylindrical gears of the 7 and 8 satellites is transmitted through the shafts of the satellites 11 and 12 to the elliptical gears of the 9 and 10 satellites, then the elliptical gears 5 and 6 of the output shaft, and then the output shaft 3 itself, for a given size ratio, the output shaft 3 through the full revolution of the input shaft 2 is in the same position and however thanks to the variable gear ratio elliptic gears 9 and 10 of satellites and elliptical gears 5 and 6 output shaft reciprocates rotational movement.

The inventive mechanism for converting motion can be used in various devices where the conversion of rotational motion into a rotary-rotational motion, in particular in a rotational-rotary mixing device, is required.

Claims (1)

A rotary-to-rotational motion converter comprising a housing in which the input and output shafts are coaxially mounted, a central stationary gear wheel fixedly mounted on the housing coaxially with the input shaft, two identical elliptical gear wheels of the same size, rotated relative to each other, are mounted on the output shaft 180 °, two identical satellites spaced 180 ° apart, each satellite consists of a cylindrical gear and an elliptical gear connected by a shaft, carrier, fixed on the input shaft, and at the ends of the carrier in the rotational kinematic pairs the shafts of both satellites are fixed, the central stationary gear wheel is in external engagement with the cylindrical gears of both satellites, and each elliptical gear wheel of the output shaft is engaged with one of the elliptical gear of the satellites, except Moreover, the spur gears of the satellites and the central fixed gear are made with the same diameters, and both elliptical gears are made of the same p dimensions with elliptical gears of the satellites, in addition, the elliptical gears of the satellites and the elliptical gears of the output shaft are mounted on their shafts so that the axis of rotation of the shaft passes through a point called the focus of the pitch ellipse of the elliptical gear wheel of the output shaft or the elliptical gear of the satellite, which is located on a large semi-axes of the dividing ellipse at a distance c from the center of the dividing ellipse $$c=\sqrt{a^2-b^2},$$

where a and b are the major and minor semi-axes of the dividing ellipse, respectively, thus achieving continuity of their engagement.

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