RU2552403C2 - Device for conversion of rotational movement to reciprocating movement and vice versa - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: device relates to machine building and can be used in devices for conversion of the rotational movement in the reciprocating movement and vice versa. The device for movement conversion contains two cylindrical wheels with outside engagement and four similar fixed tooth-wheels with internal engagement; satellite gears with secured on them planks; pinion carriers; piston rods; pistons and correcting weights. Elements installation is completely balanced.

EFFECT: improved dynamic characteristics of the device, increased durability, reliability and efficiency.

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Description

The invention relates to mechanical engineering, in particular to devices for converting rotational motion into reciprocating and vice versa, and can be used, for example, in internal combustion engines, compressors, pumps.

Known gear-lever Converter rotational motion in a reciprocating patent No. 2365799 of the Russian Federation [1]. It contains a rack, a shaft carrying a pinion gear with external teeth, a wheel with external teeth with an eccentric axis, a kinematic chain that provides a constant center distance between the gear and the wheel, a guide link, and also a driven link that relies directly or through intermediate links to the eccentric axis gear wheels. The guide link is connected with the axis of the wheel rotational, and with the rack translational or rotational pair. The gear and wheel in addition to the gear rims contain support raceways. The kinematic chain is made in the form of a closed system of rolling bodies, including a female ring and additional rolling bodies located between the gear and the ring. Additional rolling bodies can be made smooth or toothed. To balance the inertial torques, the converter can consist of two transducers located on one common drive shaft and installed in antiphase. The solution is aimed at increasing the frequency of rotation of the crankshaft with constant dimensions of the structure, ensuring the location of several driven links in the same plane.

The disadvantages of this design (patent No. 2365799) are:

1. the bulkiness of the structure, creating the impossibility of its full balancing;

2. in the claims it is written: "the gear and wheel, in addition to the gear rims, contain support raceways that coincide or are close to their initial surfaces." This phrase itself proves the impossibility of precise balancing;

3. from figure 3 it is seen that the masses of links 5 are not balanced by anything;

4. from figure 4 it is obvious that there are unbalanced moments;

5. in FIG. 1 and FIG. 3, a contradiction: the condition d ₇ / d ₃ = 2 in FIG. 1 is met, and in FIG. 3 is not met, which is unacceptable.

It is also known "Balanced device for converting rotational motion into reciprocating and vice versa", patent 2267674 (13) of the Russian Federation [2]. It contains a housing in which the body of revolution is placed in the form of a flywheel, fixed from displacement along the axis of rotation, a closed helical groove is made on the side surface of the slide, a leash is placed between the slide and the body of rotation, one part of which is fixed in the flywheel, and the other part is recessed in the closed helical groove of the slide, the rotation of the slide relative to the housing is limited by a spline connection. The essence of the invention lies in the fact that along the axis of rotation of the flywheel, an additional slider similar to the first is placed opposite the slider, while the leads of the main and additional slider are fixed in the flywheel with an offset, or the additional slider is rotated so that when the flywheel rotates, the sliders move in opposite directions. The technical result consists in balancing the inertia forces of the reciprocating motion of the sliders.

The disadvantages of the design (patent No. 2267674 (13) of the Russian Federation) are: 1) cumbersome; 2) the sliders 4 and 5, moving against each other in opposite directions, as shown in the drawing, do not move in one line, so they create an unbalanced moment of inertia forces; 3) leashes 11 and 12 are unbalanced; 4) when the slider 4 reaches the extreme left position, and the slider 5 of the extreme right position, the leads 11 and 12 transition to the reversible branches of the helical grooves, i.e. on branches having the opposite direction, in this case, of course, dynamic loads arise; 5) the inner diameter of the flywheel (flywheel shaft) cannot be too large (dimensionless), i.e. it limits the possibilities of using this mechanism for its intended purpose.

The closest in technical essence to the proposed mechanism for converting rotational motion into reciprocating and vice versa is the “Device for converting rotational motion into reciprocating and vice versa” (RF patent 2471099 [3]). The essence of this invention is as follows. The device comprises a stationary internal gear, a carrier, a frame, two pieces each with correspondingly equal masses of each other: satellites, disks, connecting rods and pistons. Disks are rigidly attached to the satellites. The number of teeth of each satellite is two times less than the number of teeth of a fixed gear wheel of internal gearing. At the reciprocating points of the disks, connecting rods are pivotally attached to them, at their second ends they are pivotally connected to the pistons. The centers of gravity of the masses of the connecting rods and pistons constantly, namely at rest and in motion in space, mutually balance each other. At equal distances from the axis of rotation of the carrier at both ends of it are the axis of rotation of the satellites and the disks rigidly attached to them for mutual balancing of the rotational masses.

The disadvantages of this design (RF patent 2471099 [3]) are the large lengths of each connecting rod: 2R plus the distance equal to two rim thicknesses of the fixed gear and again plus 2R of the fixed gear; 2) a complex configuration of the connecting rods - they should be made curved along the horizontal line where the size is 2R for the second time in order to arrange the mass of the connecting rod in one line; 3) both connecting rods in a vertical plane must also be made curly, so that during their operation they do not stall when they meet with the continuation of the carrier. From the noted shortcomings, it can be seen that the weight of the connecting rods increases significantly, and there are also difficulties in locating their centers of mass on the same line.

The above disadvantages of analogues and prototype are completely eliminated in the four-cylinder device proposed in this application, the mechanism for converting rotational motion into reciprocating and vice versa.

The technical problem is the simplicity of the design, its trouble-free operation, the complete dynamic balance of the mechanism for converting rotational motion into reciprocating and vice versa by the method of self-balancing and an increase in fly masses in order to reduce speed fluctuations.

The technical result is achieved by the fact that the mechanism of conversion into reciprocating motion and vice versa contains a frame and two pieces of identical and correspondingly equal masses of shafts 2 ′ and 3 ′, gears 2 and 3 of external gearing, satellites 4 and 7 with straps 4 ′ and 7 ′, drove H ₁ and H ₂ with corrective weights 10 and 11, connecting rods 5 and 8, pistons 6 and 9, the number of teeth of each satellite is two times less than the number of teeth of a fixed internal gear wheel, at the reciprocating points of the bars B and In ′ they are articulated s 5 and 8. In addition on the extension shaft fitted still the same two fixed gears 1 ''', 1 ^IV, deployed relative to the first pair by 180 °, are meshed with a pair of satellites 12 and 13 with the strips 12' and 13 ', rigidly attached to them and driven by carriers H _{1 ″} and H _{2 ″} with corrective masses 18 and 19, at the reciprocating points of the bars B ″ and B ″, the connecting rods 14 and 15 are pivotally attached, and the pistons 16 and 17 are connected to them .

In general, the mechanism contains four pieces of identical stationary gears of internal gearing, satellites with trims, drove, connecting rods, pistons and corrective masses, which are completely self-balanced by placing them in antiphase to each other on the same lines.

Corrective masses 10, 11, 18, 19 are installed on the extensions of the respective carriers H _{1 ′} , H _{2 ′} , H _{1 ″ ″} , H _{2 ″ ″} . Corrective weights and trims should be installed so that l ₂ > l ₁ . Imbalances of corrective masses 10 and 11; 18 and 19 should be equal to the imbalances of the respective satellites with strips 4 with 4 ′; 7 s 7 ′; 12 s 12 ′; 13 s 13 ′, and the centers of gravity of their masses are always on the same lines in antiphase. It is advisable to design H ₂ = H _{2 ′} ; H ₁ = H _{1 ′} ; H _{1 ″} = H _{1 ′ ′ ′} ; H _{2 ″} = H _{2 ′ ′ ′} .

The number of teeth of each fixed gear wheel of internal gearing 1 ′, 1 ″, 1 ″ ″, 1 ^IV (Fig. 1) is twice as many as the number of teeth of each satellite 4, 7, 12, 13, as a result, there are points on the pitch circles of the satellites , as well as opposite them on the slats of points B and B ′, B ″ and B ″ ″, making reciprocating movements in antiphase to each other. In kinematic pairs B and B ′, B ″ and B ′ ′ ′, one ends of the connecting rods 5 and 8; 14 and 15 are pivotally connected to the trims, and their other ends are connected to the piston pins at points C and C ′; C ″ and C ″ ″ of the pistons 6 and 9; 16 and 17. The masses of pistons and connecting rods are equal to each other. They move back and forth in antiphase to each other, mutually balancing the inertia forces of the translational masses. In the proposed design of the mechanism, the connecting rods have no rotational movement, therefore there is no moment of inertia forces and there is no need to balance it.

Figure 1 presents the mechanism for converting rotational motion into reciprocating and vice versa, which includes:

1 - frame;

1 ′ - stationary gear wheel of internal gearing;

1 ″ - stationary gear wheel of internal gearing;

1 ′ ′ ′ - stationary gear wheel of internal gearing;

1 ^IV - motionless gear wheel of internal gearing;

2 - a cylindrical gear wheel of external gearing;

3 - a cylindrical gear wheel of external gearing;

2 ′ - shaft;

3 ′ - shaft;

4 - satellite and 4 ′ rigidly attached to it;

5 - a rod;

6 - the piston;

7 - satellite and the bracket 7 ′ rigidly attached to it;

8 - connecting rod;

9 - a piston;

10 - corrective mass;

11 - corrective mass;

12 - satellite and rigidly attached to it strap 12 ′;

13 - satellite and rigidly attached to it strap 13 ′;

14 - a rod;

15 - connecting rod;

16 - a piston;

17 - a piston;

18 - corrective mass;

19 - corrective mass.

. В другую же, противоположную им сторону вращаются с угловой скоростью - $${\omega }_{H2}$$

все вместе: цилиндрическое зубчатое колесо внешнего зацепления 3, вал 3′, водило Н₂, его продолжение Н_2′ с закрепленной к нему гайками корректирующей массой 11 и водило Н_2″, его продолжение Н_2′′′ с закрепленной к нему гайками корректирующей массой 19. $${\omega }_{H_1}=-{\omega }_{H_2}$$

. Сателлит 4 находится в зацеплении с неподвижным зубчатым колесом 1′ внутреннего зацепления, а сателлит 7 - с таким же колесом 1″. Числа зубьев колес 1′, 1″, 1′′′, 1^IV равны между собой: $$Z_{1\text{'}}=Z_{1"}=Z_{1\text{'}\text{'}\text{'}}=Z_{1^{IV}}$$

и сателлитов 4, 7, 12, 13 тоже равны: Z₄=Z₇=Z₁₂=Z₁₃ и, кроме того, Z_1′=2Z₄, Z_1″=2Z₇, Z_1′′′=2Z₁₂, $$Z_{1^{IV}}=2Z_{13}$$

, а также R=2r, поэтому точки на делительных окружностях (прямо на зубьях сателлитов) и напротив них на планках точки В и В′; В″ и В′′′ совершают в противофазе друг другу возвратно-поступательные движения по одним и тем же горизонтальным линиям СС′ и С″С′′′, точно так же двигаются присоединенные к ним шатуны 5 и 8, поршни 6 и 9, шатуны 14 и 15, поршни 16 и 17, взаимно друг друга уравновешивая.The mechanism for converting rotational motion into reciprocating and vice versa works as follows. Spur gear wheel 2, shaft 2 ′, carrier H ₁ , its extension H _{1 ′} with a corrective mass 10 fixed to it with nuts and its carrier H _{1 ″} , its extension H _{1 ″} , its continuation H _{1 ″ ”} with corrective mass 18 attached to it nuts - together they rotate in the same direction at the same angular velocity $${\omega }_{H_{\mathrm{one}}}$$

. On the other side, opposite to them, they rotate with angular velocity - $${\omega }_{H2}$$

all together: a cylindrical gear wheel of external gearing 3, a shaft 3 ′, drove H ₂ , its extension H _{2 ′} with a corrective mass 11 fixed to it with nuts and its carrier H _{2 ″} , its continuation H _{2 ″,} with a corrective nut fixed to it weighing 19. $${\omega }_{H_{\mathrm{one}}}=-{\omega }_{H_2}$$

. Satellite 4 is meshed with a fixed gear wheel 1 ′ of internal gearing, and satellite 7 is with the same wheel 1 ″. The numbers of the teeth of the wheels 1 ′, 1 ″, 1 ′ ′ ′, 1 ^IV are equal to each other: $$Z_{\mathrm{one}\text{'}\text{'}}=Z_{\mathrm{one}"}=Z_{\mathrm{one}\text{'}\text{'}\text{'}\text{'}\text{'}\text{'}}=Z_{{\mathrm{one}}^{IV}}$$

and the satellites 4, 7, 12, 13 are also equal: Z ₄ = Z ₇ = Z ₁₂ = Z ₁₃ and, in addition, Z _{1 ′} = 2Z ₄ , Z _{1 ″} = 2Z ₇ , Z _{1 ″ ′} = 2Z ₁₂ , $$Z_{{\mathrm{one}}^{IV}}=2Z_{13}$$

, and also R = 2r, therefore, points on dividing circles (directly on the teeth of the satellites) and opposite them on the bars of points B and B ′; In ″ and B ″ ″ perform in opposite phase to each other reciprocating movements along the same horizontal lines SS ″ and C ″ C ″ ″, the connecting rods 5 and 8, pistons 6 and 9 attached to them also move connecting rods 14 and 15, pistons 16 and 17, balancing each other.

At equal distances from the axes, drove O ₁ and O _{1 ′} distances to H _{1 ′} and H _{2 ′} , also from O ₁ and O _{1 ′} - to H _{1 ″ ’} and H _{2 ″ ″} and with them the correction masses rotate 10 and 11; 18 and 19, whose masses are equal to each other. Their imbalances are respectively equal to the imbalances of the satellite 4 with the strap 4 ′ attached to it and the satellite 7 with the strap 7 ′ attached to it, in the same way - for the satellite 12 with the strap 12 ′ attached to it and for the satellite 13 with the strap 13 ′ attached . Thus, they completely balance the rotational masses. The centers of gravity of the corrective masses 10 and 11; 18 and 19 and the corresponding satellite blocks with straps all the time rotate in antiphase with each other.

As the calculations and experiments have shown, the economic efficiency of the mechanism for converting rotary motion into reciprocating and vice versa consists in failure-free operation, increased durability due to the fact that the pressure angles of the connecting rods on the cylinder walls are zero. Due to the complete dynamic balance, the quality indicators of the mechanism have significantly improved: the complete absence of harmful vibrations, noise, power loss, increased speed, efficiency and productivity. In addition, due to an increase in constant rotational masses, the flywheel moment increased, which led to a significant decrease in velocity fluctuations.

Claims (1)

The mechanism for converting rotational motion into reciprocating and vice versa, containing a frame and two pieces of the same masses of shafts, stationary gears of internal gearing, cylindrical gears of external gearing, satellites with brackets attached to them, drove with corrective masses, connecting rods, pistons, the number of teeth of each satellite is two times less than the number of teeth of a fixed wheel of internal gearing, at the reciprocating points of the slats to them hinge connecting rods are attached, characterized in that on the extension of both shafts there are still the same two fixed gears, rotated 180 ° relative to the first pair, likewise engaged with a pair of satellites with brackets rigidly attached to them, and driven from with adjusting masses, connecting rods are pivotally attached to the reciprocating points of the slats, and pistons are attached to them, thus, the mechanism contains four pieces of identical stationary gears of internal gearing, satellites with trims, drove, connecting rods, pistons and corrective masses that are completely self-balanced by the arrangement.