RU2475663C1 - Oscillatory mechanism of high-torque variator of non-friction type - Google Patents

Abstract

FIELD: machine building.

SUBSTANCE: mechanism includes a housing, an input shaft and an oscillatory shaft that is perpendicular to it, which are installed on bearings in the housing, as well as wobble plate mechanism. The latter includes a bell crank, which is put on trunnions of input shaft, forced inclination angle variation device of bell crank relative to the axis of input shaft, and a wobble plate forming together with the bell crank a rotating pair. A support fork interacting with the wobble plate by means of trunnions is installed in the housing with possibility of rotation. Oscillatory shaft is provided with a balance arm, and wobble plate is provided with a tubular guide having the possibility of being rotated and crossing the bell crank axis at right angle; a ball roller is arranged in the above guide and forms a back-and-forth pair together with the balance arm.

EFFECT: simplifying the design and improving operating characteristics of the mechanism.

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Description

The present invention relates to the field of mechanical engineering and is intended to convert the unidirectional rotation of the input link of the mechanism into oscillatory rotation of the output link with a smoothly varying swing of its oscillations, which can be used in high-torque non-friction type variators, volumetric adjustable hydraulic machines and other devices with high transmitted power.

Known oscillatory mechanisms with a continuously variable swing range of the oscillatory shaft, which is the output link of the mechanism. Such a mechanism is a necessary device in high-torque non-friction type variators. For example, cam oscillation mechanisms are known that ensure uniform rotation of the output shaft of high-torque variators [1-3], and structurally simpler non-cam oscillation mechanisms, for example [4], do not provide high uniformity of rotation of the variator output shafts. Also known mechanisms with a swash plate, in which the angle of the position of the washer relative to the axis of the input shaft is forced to change on a working mechanism [5 and 6].

We take for the prototype the closest oscillating mechanism [7], which is closest in technical essence and the achieved result, containing a housing, an oscillating shaft mounted on bearings in the housing and an oscillating shaft perpendicular to it, a swash plate mechanism, including a crank mounted on the axles of the input shaft, in in the form of a sleeve, a device for forcibly changing the angle of inclination of the crank relative to the axis of the input shaft and forming with the crank a rotational-translational pair of a swinging washer connected by the trunnions of the washer with an individual shaft by means of a support fork made on it with the possibility of providing one of the central axes of the swash plate, moving in the plane of the axis of the input shaft.

Signs of a known mechanism (prototype), coinciding with the claimed invention, are as follows. The known mechanism comprises a housing mounted on bearings in the housing of the input shaft and with an axis perpendicular to the axis of the oscillating shaft, as well as a swinging washer mechanism, including a crank mounted on the pins of the input shaft, a device for changing the angle of inclination of the crank relative to the axis of the input shaft and forming with a crank a rotary pair of a swash plate connected to the housing with the possibility of providing one of the central axes of the swash plate movement in the plane of the axis of the input shaft, for example, by w installed on a bearing in the housing perpendicular to the axis of the input shaft rotation axis supporting fork connected with trunnions swash plate washer.

In the known mechanism, the vibrational shaft at dead center has insufficient stand to ensure high uniformity of rotation of the output shaft of the high-torque variator, and since the mechanism has one vibrational shaft, a couple of such mechanisms are required for the variator, which complicates the design of the variator.

The purpose of the invention is to simplify and reduce the cost of design with improved performance.

The proposed oscillatory mechanism has the following essential features. It contains a housing, an input shaft mounted on bearings in the housing, and an oscillating shaft intersecting with it at right angles, as well as a swing washer mechanism, including a crank mounted on the axles of the input shaft, a device for forcing the angle of inclination of the crank relative to the axis of the input shaft and forming crank a rotary pair of a swinging washer connected to the housing with the possibility of providing one of the central axes of the swinging washer moving in the plane of the axis of the input shaft, for example, using mounted on a bearing in a housing connected by pins with a swinging washer of the support fork, with an axis of rotation perpendicular to the input shaft, while the oscillating shaft is equipped with a beam, and on the swinging washer a tube guide is mounted that rotates at right angles to the axis of the crank, with spherical roller forming a translational-rotational pair with the beam.

Distinctive features of the prototype features of the invention are the following. The input and vibrational shafts are mounted intersecting, the vibrational shaft is equipped with a beam, and a tubular guide with a spherical roller placed in it and forming a translational-rotary pair placed in it, mounted on the swinging washer, is rotatably mounted at a right angle with the crank axis.

Figure 1-7 given a design option of the proposed oscillatory mechanism; on Fig graphs γ (α) and φ (α); Figures 9-12 show an example of the use of an oscillatory mechanism in a high-torque non-friction type variator; 13 and 14 show the kinematic characteristics of the variator; on Fig - graphs of Ω (β) and M (β); in Fig.16 is an embodiment of the input shaft.

The proposed mechanism (Figs. 1-7) comprises a housing 1 mounted on bearings in a housing with a Z axis, an input shaft 2 and an oscillating shaft 3 intersecting with it at a right angle with a beam 4 (X ₁ is the axis of the oscillating shaft), as well as a swinging mechanism washers, including a crank 6 mounted by means of two pins 5 of the input shaft (z is the axis of the crank intersecting the Z axis at the point O) and a swinging washer 8 with cylindrical eyes 9 with spikes 10 mounted on the bearings 7 of the crank and mounted on it with rotation with AB axis, crossing scheysya with the axis with the spherical roller z crank at a right angle, the tubular guide 12. About 11 - the center of the swash plate, Oxyz - associated with the swash plate of the Cartesian coordinate system. A counterweight 13 is made on the swinging washer 13 and coaxially on the washer axis x a pair of pivots of the washer 14, and two cups 15 of bearings 7 are coaxially mounted. The support fork 16 is mounted in the housing for rotation and interacts with the swinging washer by means of the washers 14, Y the axis of rotation of the support fork passing through the center O perpendicular to the axes Z and x, OXYZ is the Cartesian coordinate system connected to the body.

The mechanism is equipped with a device for forcibly changing the angle β of the inclination of the z-axis of the crank 6 relative to the Z axis of the input shaft 2. This device contains a screw pair forming a screw 17 with a control handle 18 and a nut 19 mounted on the housing. A slider 20 is mounted on the screw with the possibility of rotation with axial locking, connected by a pin 21 with a turn signal 22. In the turn signal, a rectangular groove 23 and a cylindrical pin 24 are made, a bar 25 is placed in the groove for rotation in the crank 6, forming a translational pair with the turn signal. The turn signal 22 with the slider 20 is installed inside the input shaft with the possibility of axial movement due to the guide 26 and the cylinder 27, while the turn signal is fixed from rotation relative to the input shaft of the flat guide 28.

The mechanism operates as follows. The input shaft 2, rotating with an angular speed ω, together with the crank 6 informs the swinging washer 8 of the motion relative to the fixed center O. The nature of the movement of the various points of the swinging washer depends on their position. Movement of points on the x axis is possible only in the OXZ plane, due to the kinematic connection with the support fork 16. α is the angle of rotation of the input shaft. The oscillatory rotation of the oscillating shaft 3 with an angular velocity ω _{ka is} carried out from the swinging washer through the beam 4, interacting with the ball roller 12, mounted in the tubular guide 11. This design feature allows you to move the contact point E in the Central plane Oxy of the swinging washer, which affects the nature of the vibrations vibrational shaft, that is, on the function of the angle of rotation γ _a (α), which depends on the parameters of the mechanism (see figures 1, 4 and 5):

1) the position of the vibrational shaft 3 (Y _D );

2) the position of the rocker arm 4 (X _D , τ);

3) the orientation of the axis AB of the tubular guide 12 (y _A and µ).

The amplitude of the oscillation shaft λ = 2 | γ _a | _max depends on the angle β of the inclination of the z-axis of the crank 6 to the Z axis of the input shaft, which can be changed by rotating the control handle 18. In this case, the screw 17 moves along the axis of the input shaft together with the slider 27 and the turn signal 22. The turn signal has its rectangular groove 23 in contact with the bar 25, rotate the crank. When β = 0, the speed of the vibrational shaft ω _ka = 0, and with the maximum movement of the screw h, the angle β _max and the amplitude of the oscillations λ are maximum.

The dependence of the angle of rotation of the vibrational shaft γ _a (α) during a half-turn of the input shaft is shown in Fig. 8, where the dashed line shows the function of the angle of rotation of the support fork φ (α) at β = 28.8 °. φ is the angle of rotation of the oscillatory shaft in the mechanism [7], adopted as a prototype. The graphs presented show that in the vicinity of the dead center k we have a relatively longer dwell time of the vibrational shaft of the proposed device than the prototype, since the curvature γ _a (α = 90 °) is less than the curvature φ (α = 90 °). This allows you to have less than two times less than the prototype uneven rotation of the output shaft of the variator when using the proposed mechanism.

The oscillation shaft mounted symmetrically shown in figure 4, has a 90 ° phase-shifted kinematic characteristics. The rotation angle of this vibrational shaft γ _b (α) is shown in Fig. 8. This property allows the proposed mechanism to be used in a high-torque non-friction type variator with one swinging washer and with a pair of vibrational shafts 3a and 3b. The design of such a variator is shown in FIGS. 9-12, where 2 is the input shaft and 29 is the output shaft. A differential is mounted on the output shaft with a pair of gears 30 mounted for relative rotation, and a carrier 31 with a satellite 32 coupled to the gears is fixed on this shaft. On the dowels 33 of each of the gears, a pair of overrunning clutches 34 are planted with leading coupling halves 35 and 36, made in the form of pulleys. On each oscillating shaft, a pair of pulleys 37 and 38 are made, connected to the leading coupling halves 35 and 36, respectively, fixed to the pulleys with cables 39, with the possibility of transmission from the oscillating shafts through overrunning clutches of unidirectional rotation to the gear wheels with speeds

ω _a = | ω _ka | (r / R) and ω _b = | ω _kb | (r / R),

where r and R are the radii of the pulleys (figure 10).

The speed drove 31 differential, therefore, the output shaft 29 of the variator

Ω = 0.5 (ω _a + ω _b ).

The coefficient of uneven rotation of the output shaft

,

,

- среднее значение скорости выходного вала;Where

- the average value of the speed of the output shaft;

M is the moment transmitted by the output shaft.

The non-uniformity coefficient δ substantially depends on the parameters of the oscillatory mechanism (Fig. 13). The minimum value δ = 0.07 is achieved when the angle of inclination of the axis AB of the cylindrical guide µ = 30 °.

On Fig are given the kinematic parameters of the variator at an input shaft speed of n = 1000 rpm (ω = 104.7 rad / s) and β = 20 °.

When the angle β changes from 0 ° to 20 ° with the control handle 18, the transmitted moment M and the speed Ω of the output shaft 29 vary from 0 to 18.4 rad / s, and in stop mode (at β ~ 0 °) we have a peak transmitted moment M _st (Fig. 15).

The use of the proposed oscillatory mechanism in a high-torque non-friction type variator allows to simplify its design due to the absence of complex cam oscillation mechanisms [1-3], while ensuring a sufficiently high uniformity of rotation of the output shaft, which can be reduced to zero due to overtaking in overrunning clutches. Due to overtaking (Fig. 15), the variator gear ratio is automatically changed (self-regulation effect [8 and 9]): when the transmitted moment M decreases, the speed of the output shaft Ω increases with the fixed control handle 18.

Static balancing of the mechanism is carried out by a counterweight 13 on a swinging washer, and dynamic - by using two flywheels 40 and 41, planted at the ends of the input shaft 2 (Fig. 16).

In variators of this type, gear non-friction overrunning clutches [10-12] should be used, in which the response angle is zero for a large transmitted moment.

Information on high-torque variators of non-friction type is given on the site [13].

Information sources

1. DE 3309044, F16H 29/08, 03/14/83.

2. RU 2242654 C2, F16H 29/08, 01/20/2003 (B.V. Pylaev).

3. RU 2409779 C1, F16H 29/08, 07/06/2009 (B.V. Pylaev).

4. RU 2250400 C1, F16H 29 / 08.06.10.2003 (B.V. Pylaev).

5. DE 2659958, F16H 23/08, 07/30/07.

6. SU 1096417 A, F16H 23/04, 03.06.82.

7. RU 2207463 C2, F16H 23/04, 03/06/2001 (B.V. Pylaev).

8. RU 2313019 C2, F16H 29/08, 12/28/2005 (B.V. Pylaev).

9. B.V. Pylaev. Adaptability of non-friction high-torque variator to external load // Bulletin of mechanical engineering. 2009. No5. S.12-16.

10. B.V. Pylaev, A.A. Shamin. Overrunning clutch for non-friction high-torque variator // Vestnik mashinostroeniya. 2008. No. 6. C.3-6.

11. RU 2353835 C2, F16D 41/08, 03/27/2007 (B.V. Pylaev, A.A.Shamin).

12. RU 2353836 C2, F16D 41/08, 03/27/2007 (B.V. Pylaev, A.A.Shamin)

13. http://vmvp.ru

Claims (1)

The oscillatory mechanism of a high-torque non-friction type variator, comprising a housing mounted on bearings in the input shaft housing and with an axis perpendicular to it, an oscillating shaft, as well as a swash plate mechanism including a crank mounted on the axles of the input shaft, a device for forcing the angle of inclination of the crank relative to the input axis shaft and forming a rotary pair with a crank swinging washer associated with the housing with the possibility of providing one of the Central axes of the swinging washer The expansion in the plane of the axis of the input shaft, for example, by means of a rotary axis perpendicular to the input shaft, mounted on a bearing in the housing, connected by pins of a washer with a swinging washer of the support fork, characterized in that the input and vibrational shafts are mounted intersecting, the vibrational shaft is provided with a beam, and on the swinging washer, a tubular guide is mounted that rotates and rotates, intersecting at right angles to the axis of the crank, with a ball roller placed in it, forming a translational-rotational rocker with the beam th pair.

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