SU1627769A1 - Balanced slider-crank mechanism - Google Patents

Abstract

The invention relates to a slider crank converter in the reciprocating movement in a reciprocal movement and will find application in particular in reciprocating machines. The purpose of the invention is to increase the reliability and durability of the mechanism by eliminating vibration during its operation. The rotation of the crank 3 through the connecting rod 6 is converted into a reciprocating movement of the slide 5 and the movement along the connecting rod curves of the rods 9 and 10 of the hinge-lever balancing device. The angular velocities of the rods 9 and 10 are always equal and opposite to the angular velocities of the crank 3 and the connecting rod 6. Therefore, the main vector and the main moment of inertia of the links of the mechanism are zero for any law of rotation of the crank. 2 Il. (L with U & to vj about to

Description

1

The invention relates to mechanical engineering, namely to crank-and-slide converters of rotational movement into reciprocating,. and can be used in particular in reciprocating machines.

The purpose of the invention is to increase the reliability and durability of the mechanism by eliminating vibration during its pa-JQ bot.

FIG. Figure 1 shows a kinematic diagram of a mechanism with a pivot-lever balancing device in the form of a rhomboid; in fig. 2 - the same, with an equalizing device in the form of an anti-parallelogram.

The mechanism comprises a rack 1 with a straight-line guide 2, mounted on a rack 1, a crank 3, 20, a hinge 4 connected to it, mounted in a guide 2, a slider 5, a connecting rod 6, one end through a hinge 7 connected with a slider 5, and the other end through the hinge b is connected with the crankshaft 25 of the number 3, and the hinge balancer device in the form of short and long rods 9 and 10, respectively, connected by a common hinge 11. The other end of the shafts 9 through the hinge 12 is connected with crank 3, and the rod 10 through the hinge 13 is connected with connecting rod 6 (fi 1) or by the other end, the rod 9 is connected to the connecting rod 6 through the hinge 13, and the rod 10 through the hinge 12 is connected to the crank 3 (Fig. 2). The length of the rod 9 is equal to the distance between the hinges 8 and

12 on crank 3, and the length of the rod 10 is equal to the distance between the hinges 8 and.

13 on the connecting rod 6 so that, depending on the location of the common joint 11, the rods 9 and 10 are formed by the corresponding segments of the crank 3 and the connecting rod 6 of the rhomboid (Fig. 1) or the parallel-parallel, with the frame (Fig. 2). The lengths of the crank 3, the connecting rod 6 and the rods 9 and 10 are chosen such that the ratio of the length of the crank 3 to the length of the gauge 6 is equal to the ratio of the length of the rod, n 9 to the length of the rod 10. The geometric shape of the crank 3 and the connecting rod 6 allows you to shift the hinges 12 and 13 from the longitudinal axes x and x of these links. In this case, the longitudinal axis x of the cryplate 3 forms the angle Ob from the straight connecting axis of the hinges 8 and 12 and is one of the sides of the rhomboid or the anti-parallelogram. With the project35

The oC angle can be selected from 0 - 360 °.

The parameters of the mass geometry of the links of the mechanism (the masses of the links, the moments of inertia of the masses and the static moments of the masses) are determined from a system of algebraic equations

(mj + mg + mj + m), + 8, c-A cosoi 0; S, x- A sinei 0; S2u + tg1g + V14G3 cosoi 0;

about;

i S2) f + B14C sin 06

five

0 5 o

with

five

o;

° ty ° 4X aH chh

S ЈU + 14 1 j 0,

I, + (m, + m1 + m, + m4) 1 (+ m} (S4, .-) 21, cos Oi - I, O; I4 + m2l + m4lj - I4 0,

where m., m, t, t4 of the mass, respectively, of the connecting rod, slider, short rod and long rod; SU.

54d, 55d - static moments of the masses, respectively, of the crank, connecting rod, slider, short rod and long rod relative to the longitudinal axes of these links;

, lj-s,

 - for the mechanism in FIG. one;

 + S4 (j,

  for mechanism on

%, 8P, 8, V H

1, 1g, I., I4

FIG. 2;

-static moments of mass, respectively, of the crank, connecting rod, slider, short rod and long rod relative to the transverse axes of these links;

- moments of mass inertia, respectively, of the crank, connecting rod, short rod and long rod relative to the points of intersection of the longitudinal and transverse axes

B

these links (hinges A, 8,12 and 13);

21G +

ten

20

25

- the lengths of the crank, connecting rod, short rod and long rod, respectively; 06 is the angle between the longitudinal axis of the crank and the side of the rhomboid or the anti-parallelogram that belongs to it.

When designing a mechanism, the value of any seven of the eighteen mass geometry parameters included in the system of equations is constructively specified.

The mechanism works as follows.

The rotation of the crank 3 through the crank 6 is converted into a reciprocating movement of the slider b and the movement along the connecting rod curves of the rods 9 and 10. At the same time, the diagonals of the rhomboid or the anti-parallelogram perform translational motion, the hinges 12 and 13 move in opposite directions to their diagonal, along the length, the rhomboid or anti-parallelogram sides are rotated towards each other. As a consequence, the angular velocity of the rod 9 is equal and opposite to the angular velocity of the crank 3, and the angular velocity of the rod 10 is equal to and opposite to the angular velocity of the connecting rod 6

From FIG. 1 it is obvious that Cp3

+ tf-U, 4 m - -CH of the IG 2, it is obvious that lfj, Lp4 2fi + (- (JL. To the differential, these time dependencies, in both cases, get (0} -CO ,, Y4 J4 .45

Consequently, in the mechanism performed according to the proposed schemes, the main vector and the main moment of inertia forces of the links of the mechanism are equal to zero for any law of rotation of the crank, i.e. the mechanism is fully balanced under all conditions and modes of operation.

jj

thirty

35

40

Claims (1)

Invention Formula  A balanced crank-slider mechanism containing a rack with a straight rail, a crank mounted on a rack, mounted in a slide rail, a connecting rod hinged at its ends with a crank and a slider, and a hinged-lever balancer in the form of two rods of different lengths, one end through a common hinge of related between each other, and the other ends of the hinged ends are short with a crank, and long with a connecting rod, the ratio of the lengths of the short and long rods being equal to the ratio j of the lengths of the crank and the connecting rod, characterized in that, in order to increase reliability and olgovechnosti, the rods form a crank and connecting rod parallelogram or rhomboid, and the mass units mechanism parameters defined by Equations m, + m2- m3 + m4) l;) + S (u-A cosoi 0; s "L5 (nO (, 0; Sju + gag1g + b141 co5 (° S2X + B14C sincxi 0; 0 five S, ELT 0; Sju 1.4 1 ° fX 50; 12 I dnj + n -Hnj + m) 1, -Hnji j (S4, .- mjl,) 21 cosod -13 0; - I4 0. four mt12 + ra414 where .t.t are the masses of the connecting rod, the ram, the short rod and the long rod, respectively; 45 50 40 five S | X S2r four Sf (}. "G" the static moments of the masses, respectively, of the crank, connecting rod, slider, short rod and long rod relative to the longitudinal links of these links, the static moments of the masses, respectively, of the crank, the connecting rod, the slider, the short rod and the long rod relative to the transverse axes of these links; ,, Ј,., I - moments of inertia masses, respectively, of the crank, connecting rod, short rod 5 and long rod about the intersection points of the longitudinal and transverse axes of these links; | , 1, Ц, 1ц are the lengths of a crank, a connecting rod, a short rod and a long 15 rod, respectively; O - the angle between the longitudinal jig -SijiJ ,, lj the axle of the crank and the side belonging to it of a rhomboid or anti-parallelogram; - for a mechanism with a balancing device in the form of a rhomboid; m44 + S41} .jlj-s i. for a mechanism with a balancing device in the form of an anti-parallelogram. B at H 11 X5 13 6 FIG. I GGTH U 512 g