RU2603045C2 - Eight cylinder mechanism converting rotary motion into reciprocating movement and vice versa - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: invention relates to mechanisms converting rotary motion into reciprocating movement and vice versa. Eight cylinder movement conversion mechanism includes four cylindrical wheels of external gearing, round shafts and eight fixed internal engagement gear wheels, carriers, satellites, to each satellite is rigidly attached disk, eight con-rods and eight pistons. In the back-and-forth points of discs rods are hinged to them, which are hinged to pistons by their ends. On carriers extension there are installed correction masses.

EFFECT: higher efficiency.

1 cl, 3 dwg

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 transducer of rotational motion in a reciprocating patent, Patent No. 2365799, RF [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 interaxial distance of the gear and wheel, a guide link, and also a driven link that leans 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 the drawings: 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 not permissible.

It is also known "Balanced device for converting rotational motion into reciprocating, and vice versa", patent 2267674, RF [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 opposite the slider an additional slider is placed, similar to the first, 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, RF) 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 mechanism for converting rotational motion to reciprocating and vice versa, which we propose in this application, is the “Device for converting rotational motion to reciprocating and vice versa” (patent 2471099, RF [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, rods are pivotally attached to them, at their second ends they are pivotally attached 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 (patent 2471099, RF [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.

As the closest analogue (prototype) selected device for converting rotational motion into reciprocating and vice versa, patent RU No. 2499934 C2, IPC F16H 19/02, F16H 21/16, publ. 11/27/2013, bull. Number 22. The prototype consists, i.e. contains two pieces of shafts, pistons, cylindrical wheels of external gearing, gears of internal gearing, satellites, a strap is rigidly attached to each satellite. At the reciprocating points of the planks, rods are pivotally attached to them, which are pivotally connected at their second ends to the pistons. On continuation of the carrier, corrective masses were installed. The invention allows to improve the dynamic qualities of the mechanism, to increase its durability, reliability, performance.

The disadvantages of the closest analogue (prototype) include the fact that they solved the problems of balancing, increasing efficiency, strength, durability, lowering the consumption of fuels and lubricants, etc. only for two-cylinder devices, and not an eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa. In addition, the prototype develops power 4 times less than the proposed mechanism for this invention.

The elimination of these disadvantages is solved in the application for the invention of an eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa.

An object of the invention is trouble-free operation, complete dynamic balance of the eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa, lowering the friction coefficient, preventing jamming, increasing power, strength, durability, efficiency, lowering material consumption.

The problem is solved in the development of the ideas embodied in the prototype, namely, replacing the crankshafts with simple round ones, balancing the moments of inertia of the rods by replacing their complex plane-parallel motion with reciprocating, reducing the pressure angles of the rods on the cylinder walls to zeros, and balancing the translational masses and balancing the rotating masses. The difference with the prototype is that below is a solution to all of these complex national economic problems, not for 2-cylinder mechanisms, but for eight-cylinder ones.

, $$H_2^{\text{'}}$$

, $$H_3^{\text{'}}$$

, $$H_4^{\text{'}}$$

, $$H_5^{\text{'}}$$

, $$H_6^{\text{'}}$$

, $$H_7^{\text{'}}$$

, $$H_8^{\text{'}}$$

(фигуры 1, 2, 3).The proposed eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa is shown in the drawings: FIG. 1 is a front view, FIG. 2 is a section along A-A, FIG. 3 is a section along BB. This mechanism contains a frame 1 (figures 1, 2, 3); four identical cylindrical wheels 2; 3 (FIG. 2), 22; 23 (figure 3); round shafts: O ₁ -O ₁ , O ₂ -O ₂ , O ₃ -O ₃ , O ₄ -O ₄ (figures 1, 2, 3) and eight fixed gears of internal gearing: 1 ′, 1 ′, 1 ′, 1 ′, 1 ′, 1 ′, 1 ′, 1 ′ (figures 1, 2, 3) sequentially rigidly connected to the shafts of identical carriers: H ₁ , H ₂ , H ₃ , H ₄ , H ₅ , H ₆ , H ₇ , H ₈ (Figs. 2, 3) and identical satellites with identical trims rigidly attached to them (or disks with R _K = R _D ) 4 c 4 ′, 7 c 7 ′, 12 c 12 ′, 13 c 13 ′, 18 c 18 ′, 19 c 19 ′, 26 c 26 ′, 27 c 27 ′ (figures 1, 2, 3), to the reciprocating moving points of the bars B ₁ , B ₂ , B ₃ , B ₄ , B ₅ , B ₆ , B ₇ , B _{8 the} same connecting rods 5, 8, 17, 20, 11, 14, 28, 25 are pivotally connected figures 1, 2, 3), to the connecting rods at points C ₁ , C ₂ , C ₃ , C ₄ , C ₅ , C ₆ , C ₇ , C _{8 the} same pistons 6, 9, 10, 15, 16, 21 are pivotally attached , 24, 29 (figures 1, 2, 3), corrective masses K ₁ , K ₂ , K ₃ , K ₄ , K ₅ , K ₆ , K ₇ , K ₈ installed on the extensions of the carrier $$H_{\mathrm{one}}^{\text{'}\text{'}}$$

, $$H_2^{\text{'}\text{'}}$$

, $$H_3^{\text{'}\text{'}}$$

, $$H_{\mathrm{four}}^{\text{'}\text{'}}$$

, $$H_5^{\text{'}\text{'}}$$

, $$H_6^{\text{'}\text{'}}$$

, $$H_7^{\text{'}\text{'}}$$

, $$H_8^{\text{'}\text{'}}$$

(figures 1, 2, 3).

Reciprocating masses m _shi rods and pistons m _pi pairwise connected to each other, are formed in Σm _i and are on the same straight lines at equal distances from each other. We give them along the lines.

In figure 2 along the lines C ₁ C ₂ and C ₃ C ₄ :

Σm ₁ = m _w5 + m _p6 and Σm ₂ = m _w8 + m _p9 , Σm ₁ = -Σm ₂

Σm ₃ = m _w11 + m _p10 and Σm ₄ = m _w14 + m _p15 , Σm ₃ = -Σm ₄ .

In figure 3 along the lines C ₅ C ₆ and C ₇ C ₈ :

Σ _m5 = m _w20 + m _p21 and Σm ₆ = m _w17 + m _p16 , Σm ₅ = -Σm ₆

Σm ₇ = m _ш25 + m _п24 and Σm ₈ = m _ш28 + m _п29 , Σm ₇ = -Σm ₈ .

, $$H_2^{\text{'}}$$

, $$H_3^{\text{'}}$$

, $$H_4^{\text{'}}$$

, установлены корректирующие массы m_к1, m_к2, m_к3, m_к4, обозначенные K₁, K₂, K₃, K₄, а на продолжениях водил $$H_5^{\text{'}}$$

, $$H_6^{\text{'}}$$

, $$H_7^{\text{'}}$$

, $$H_8^{\text{'}}$$

- K₅, K₆, K₇, K₈ - массы которых m_к5, m_к6, m_к7, m_к8 (фиг.3).On the continuations drove H ₁ , H ₂ , H ₃ , H ₄ (figure 2), i.e. on $$H_{\mathrm{one}}^{\text{'}\text{'}}$$

, $$H_2^{\text{'}\text{'}}$$

, $$H_3^{\text{'}\text{'}}$$

, $$H_{\mathrm{four}}^{\text{'}\text{'}}$$

, the corrective masses m _k1 , m _k2 , m _k3 , m _k4 , designated K ₁ , K ₂ , K ₃ , K ₄ , and on the extensions continued $$H_5^{\text{'}\text{'}}$$

, $$H_6^{\text{'}\text{'}}$$

, $$H_7^{\text{'}\text{'}}$$

, $$H_8^{\text{'}\text{'}}$$

- K ₅ , K ₆ , K ₇ , K ₈ - the masses of which are m _k5 , m _k6 , m _k7 , m _k8 (figure 3).

On the axes of all corrective masses, a thread is cut. They are adjusted with nuts so that their centers of mass and the corresponding total masses of the satellites with trims (or disks) are on the same line opposite to each other. The imbalances of the satellites with trims should accordingly be equal to the imbalances of the correcting masses.

We write the equality of imbalances in figures 2 and 3:

,

,

,

,

,

,

,

,

,

,

,

,

,

,

,

,

where Q _ci - satellite gravity, i - their serial numbers,

Q _pli - the gravity of the slats, i - their serial numbers,

- плечи (фиг.2 и 3).H _i and $$H_i^{\text{'}\text{'}}$$

- shoulders (figure 2 and 3).

до планок (или дисков) (фигуры 2 и 3), т.е. l₁<l₂.To avoid jamming of the mechanism, the lengths of the axes of the correction masses l ₁ should be designed less than l ₂ - distances from horizontal common lines $$H_i-H_i^{\text{'}\text{'}}$$

to the slats (or disks) (figures 2 and 3), i.e. l ₁ <l ₂ .

The number of teeth of each satellite 4, 7, 12, 13, 17, 19, 26, 27 should be less than half the number of teeth of each fixed internal gear wheel 1 ′, 1 ′, 1 ′, 1 ′, 1 ′, 1 ′, 1 ′, 1 ′ (figures 1, 2, 3), as a result, on all satellites there are points, more precisely on their dividing circles, and also directly opposite them on the bars - B ₁ , B ₂ , B ₃ , B ₄ , B ₅ , B ₆ , B ₇ , B ₈ , reciprocating in antiphase to each other.

One ends of the connecting rods 5, 8, 11, 14, 17, 20, 25, 28 at points B ₁ , B ₂ , B ₃ , B ₄ , B ₅ , B ₆ , B ₇ , B _{8 are} pivotally connected to the bars 4 ′, 7 ′ 12 ′, 13 ′, 18 ′, 19 ′, 26 ′, 27 ′, and their other ends also at points C ₁ , C ₂ , C ₃ , C ₄ , C ₅ , C ₆ , C ₇ , C ₈ with piston fingers. The masses of all pistons of the same magnitude, as well as the masses of all connecting rods are also of the same magnitude, similarly between each other of the same mass one should choose trims, satellites. All masses must move in antiphase pairwise between each other (for complete balancing of the whole mechanism).

In figures 1, 2, 3, the proposed eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa, which includes:

1 - frame;

1 ′ - eight fixed identical gears of internal gearing, since they are motionless, they are, as it were, part of the rack, therefore they are under the same number;

2 - a cylindrical gear;

3 - a cylindrical gear;

4 - satellite with a 4 ′ bar;

5 - a rod;

6 - the piston;

7 - satellite with strap 7 ′;

8 - connecting rod;

9 - a piston;

10 - a piston;

11 - connecting rod;

12 - satellite with a bar 12 ′;

13 - satellite with a bar 13 ′;

14 - a rod;

15 - a piston;

16 - a piston;

17 - a rod;

18 - satellite with a bar 18 ′;

19 - satellite with a bar 19 ′;

20 - connecting rod;

21 - a piston;

22 - a cylindrical gear;

23 - a cylindrical gear;

24 - a piston;

25 - connecting rod;

26 - satellite with a bar 26 ′;

27 - satellite with a bar 27 ′;

28 - connecting rod;

29 - a piston;

K ₁ - correction weight;

K ₂ - correction weight;

K ₃ - correction weight;

K ₄ - corrective mass;

K ₅ - correction weight;

K ₆ - correction weight;

K ₇ - corrective mass;

K ₈ - corrective mass.

The eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa works as follows. Cylindrical wheels 2 and 3, 22 and 23 of external gearing. They have equal numbers of teeth and are engaged with each other (figures 1, 2, 3). They rotate in opposite directions in pairs with equal angular velocities:

,ω ₂ = -ω ₃ ,

,

,

,

,ω ₂₂ = -ω ₂₃ ,

,

.

.

As can be seen from figures 1, 2, 3 and from the angular velocities shown, the shafts of each row: the upper O ₁ O ₁ and O ₂ O ₂ (figure 2) and the lower O ₃ O ₃ and O ₄ O ₄ (figure 3) , rotate in opposite directions and result in the opposite rotational movement of the carriers, satellites and corrective masses rigidly connected to them.

и $$H_3^{\text{'}}$$

, вращаются все с угловой скоростью ω₂. В противоположную сторону им вращаются с ω₃ сателлиты с планками 7 c 7′ и 12 c 12′, а также корректирующие массы K₂ и K₄, установленные на продолжениях водил $$H_2^{\text{'}}$$

и $$H_4^{\text{'}}$$

.Satellites with straps 4 c 4 ′ and 13 c 13 ′, as well as corrective masses K ₁ and K ₃ installed on the extensions of the carrier $$H_{\mathrm{one}}^{\text{'}\text{'}}$$

and $$H_3^{\text{'}\text{'}}$$

all rotate with an angular velocity ω ₂ . In the opposite direction, they rotate with ω ₃ satellites with straps 7 c 7 ′ and 12 c 12 ′, as well as correction masses K ₂ and K ₄ installed on the extensions of the carrier $$H_2^{\text{'}\text{'}}$$

and $$H_{\mathrm{four}}^{\text{'}\text{'}}$$

.

и $$H_7^{\text{'}}$$

, вращаются все с угловой скоростью ω₂₂. В противоположную им сторону вращаются с ω₂₃ сателлиты с планками 18 c 18′ и 26 c 26′, а также корректирующие массы K₆ и K₈, установленные на продолжениях водил $$H_6^{\text{'}}$$

и $$H_8^{\text{'}}$$

.Satellites with straps 19 c 19 ′ and 27 c 27 ′, as well as corrective masses K ₅ and K ₇ installed on the extensions of the carrier $$H_5^{\text{'}\text{'}}$$

and $$H_7^{\text{'}\text{'}}$$

all rotate with an angular velocity ω ₂₂ . In the opposite direction they rotate with ω ₂₃ satellites with straps 18 c 18 ′ and 26 c 26 ′, as well as correction masses K ₆ and K ₈ installed on the extensions of the carrier $$H_6^{\text{'}\text{'}}$$

and $$H_8^{\text{'}\text{'}}$$

.

Thus, the centers of gravity of the correcting masses and corresponding satellite blocks with trims, the imbalances of which are calculated according to the above formulas, rotate in antiphase with each other in the same planes.

On the satellites there are progressively moving points, and opposite them on the trims are rotational kinematic pairs B1 B2, B3, B4, B5, B6, B7, B8, which make reciprocating movements in antiphase with each other together with connecting rods and pistons attached to them. We list them.

The connecting rod 5 with the piston 6 in a straight line C ₁ C ₂ move in antiphase to the connecting rod 8 and the piston 9.

The connecting rod 11 with the piston 10 in a straight line C ₃ C ₄ move in antiphase to the connecting rod 14 and the piston 15.

The connecting rod 17 with the piston 16 in a straight line C ₅ C ₆ move in antiphase to the connecting rod 20 and the piston 21.

The connecting rod 25 with the piston 24 in a straight line C ₇ C ₈ move in antiphase to the connecting rod 28 and piston 29.

As the calculations and experiments showed, the economic efficiency of the eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa consists in the failure-free operation, durability due to the fact that the pressure angle of the connecting rod on the cylinder walls is zero. As a result of the complete balance of the moving masses, the dynamic qualities of the mechanism have significantly improved: the complete absence of harmful vibrations, noise, loss of power, increased speed, efficiency and productivity. In addition, due to the links having constant values of the moments of inertia, the flywheel moment increased, which led to a significant decrease in velocity fluctuations - to a decrease in the coefficient of non-uniformity of motion δ. Using this mechanism will increase the environmental friendliness of internal combustion engines, as well as other mechanisms and machines.

Information sources

1. Patent No. 2365799 of the Russian Federation.

2. Patent No. 2267674 of the Russian Federation.

3. Patent No. 2471099 of the Russian Federation.

Claims (1)

The eight-cylinder mechanism for converting rotational motion into reciprocating and vice versa, containing a frame, two pieces of identical motionless gears of internal gearing, shafts, cylindrical wheels of external gearing, rigidly connected to the corresponding shafts of the carrier, connecting rods, pistons, satellites, with each satellite a disk is rigidly attached, at the reciprocating points of the disks, the same connecting rods are pivotally attached to them, which are oppositely located on the same line with the the pistons hinged to them, mutually balancing each other, on the continuation of both carriers corrective masses are installed, the imbalances of which are respectively equal to the imbalances of the masses of the satellites with the disks, the points of gravity of the correcting masses are adjusted so that they lie on the same line opposite to the centers the severity of the satellites with disks, fully balancing them, characterized in that it additionally contains six disks, rigidly attached to each satellite and pivotally to the connecting rods, as well as o additionally contains two pieces of identical cylindrical wheels of external gearing, round shafts, and six pieces of identical motionless gear wheels of internal gearing, connecting rods, pistons, carrier, rigidly connected to the corresponding shafts, and satellites, the number of teeth of each satellite is two times less than the number teeth of each fixed gear wheel of internal gearing, at the reciprocating points of the disks, rods are pivotally attached to them, which are located opposite to each other on the same straight lines In these lines with articulated pistons, mutually balancing each other, on the continuation of the carrier, corrective masses were installed, the imbalances of which are equal to the imbalances of the masses of the satellites with the disks, the points of location of the centers of gravity of the correcting masses are regulated so that they lie on the same straight lines opposite with the centers of gravity of their respective satellites with disks, balancing them completely.

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