Matveyev's inertial transformer

FIELD: electricity.

SUBSTANCE: invention is related to inertial transformers and may be widely used in automobile construction. The inertial transformer comprises a system of coaxial drive shaft (1) and driven shaft (2) and at least one pair of levers. The pair of levers has a common hinge joint and couples cranks of the drive (1) and driven (2) shafts, while one of the levers acts as cargo link (5). The cargo link (5) is made with the centre of mass (9) outside limits of the common hinge joint; it is installed at the crank of the driven shaft (2) and can be rotated circular when the driven shaft (2) is deaccelerated.

EFFECT: simplified design, improved resource and the range of permitted revolution and torque transferred through a pulse transformer.

6 dwg

 

The invention relates to a device for automatic approval of a limited torque and speed power source, such as an internal combustion engine with a torque load resistance that is variable within wide limits, namely inertial transformers torque and may find wide application in automotive industry and drive various machines and mechanisms.

Known inertial transformer containing a system of spatially arranged levers having a common hinge connecting the leading, intermediate and driven shafts, one of which levers is made with offset center of mass beyond the hinge, and the mechanisms of a free motion between the intermediate and driven shaft of the device (Mechanical impulse transmission. Vfemale. Third edition. Moscow. "Engineering". 1978, P.65. Fig.23.).

The disadvantage of this technical solution is the large size of the device and the transmitted torque is small because of the large number of spatially arranged levers and hinges with limited stiffness.

From this drawback (a large number of levers) free inertial transformer containing the system of coaxially located the leading, intermediate and driven shafts and at least one pair of levers having a common Sha is research, connecting the cranks of the leading and intermediate shafts, with one of the levers plays the role of a freight link, and the mechanisms of a free motion between the intermediate and driven shaft of the device (Mechanical impulse transmission. Vfemale. Third edition. Moscow. "Engineering". 1978, P.77. Fig.31.). This solution is also known as the transfer of Bali (Aeiou. Inertial auto transformers torque. Moscow. The engineering. 1978, P.13. Fig.4.), and selected as a prototype of the proposed technical solutions.

A common shortcoming of these pulse transformers is Snamprogetti the resulting torque on the intermediate shaft of the device, resulting to transmit torque in one direction requires mechanisms of free running, which is an integral part of the transformer according to this scheme (Aeiou. Inertial auto transformers torque. Moscow. The engineering. 1978, P.24. About the possibility of creating inertial transformer without mechanisms of free running.). The mechanisms of free running are the most loaded and least reliable item inertial transformer that limits the use of inertial transformers in General.

The objective of the invention is to simplify the construction, increase the of the resource and area allowable loads and inertial momentum of the transformer.

This is achieved by the fact that, in contrast to known constructions, cargo link inertia of the transformer, which is also one of the levers connecting the cranks of the leading and intermediate shafts are made with the center of mass outside the common hinge levers. The transfer of the center of mass of the cargo link leads to the fact that in the cycle of acceleration and in the cycle of deceleration of the center of mass of the cargo component of force produced on the intermediate crank shaft, oriented in the same direction, and the reverse pulse on the intermediate missing. The absence of a reverse pulse of the moment of rotation on the intermediate shaft can simplify the design of pulse transformer, eliminating the mechanisms of free running as a redundant element, and combine the intermediate and driven shaft, since their separation through the mechanisms of free travel is not required.

Technical result achieved is to simplify the construction, increase of resource and area allowable speed and torque transmitted through the pulse transformer.

Partially achieved the technical result is also that the proposed inertial transformer allows you to transmit torque in either direction - driven shaft may function as a master, and it is also possible to reversionary the direction of rotation of the shafts, not possible when using mechanisms of free running, as is the case in the known technical solutions. This option extends the scope of possible applications of the proposed inertial transformer.

The essence of the invention lies in the fact that changing the position of the center of mass of the lever - freight link leads to the fact that the forces arising on the intermediate crank shaft during acceleration and braking of freight link to be directed in one direction, and it allows you to combine the intermediate and driven shaft without using the mechanisms of a free motion. (Hereinafter, it is considered that the intermediate and driven shaft is the driven shaft). During acceleration and during deceleration of the center of mass of the cargo part of the total hinge lever is in position between the crank shaft and the center of mass of the cargo link, but from opposite sides of the path of movement of the crank shaft. During braking of the center of mass of the cargo link via a common hinge levers the center of mass of the cargo level in order to maintain the absolute speed of movement in space, tends to turn the lever - freight link around a common hinge levers, and the direction of the transmitted force of inertia of the center of mass of the opposite from the center of mass of the hinge is the same as in the acceleration of the center of mass grozovo what about the link. This effect is the coincidence of the directions of the forces acting on the crank shaft during acceleration and deceleration of the center of mass of the cargo level is reached previously unknown set of features of the system from at least one pair of levers having a common hinge connecting the cranks and output shafts, the center of mass of one of the levers is outside the common hinge levers allows to achieve the stated technical result, that is, to exclude from the design mechanisms of free running.

Despite the fact that the arm with the center of mass is outside the hinges known (Mechanical impulse transmission. Vfemale. Third edition. Moscow. "Engineering". 1978, P.65. Fig.23.), in the specified source of one of the hinge lever fixed in space and does not show the properties shown in the proposed technical solution. This allows to make a conclusion about the principal novelty and previously unknown set of features "system of at least one pair of levers having a common hinge connecting the cranks and output shafts, the center of mass of one of the levers is outside the common hinge levers", both of these designs inertial transformer for transmitting the rotation of the follower shaft in one direction are used mechanism is SMY free running.

The proposed solution is illustrated in the drawings Figure 1 - 6.

Figure 1 shows the combined section of the device in side view.

Figure 2 shows a front view of the device in section.

Figure 3 shows the kinematic diagram of the device.

Figure 4 shows the kinematic diagram of the device indicating the phase of the acceleration and braking phase common hinge levers.

Figure 5 shows a kinematic diagram of the device in the phase of acceleration of the center of mass of the cargo link.

Figure 6 shows the kinematic diagram of the device in the braking phase of the center of mass of the cargo link.

Figure 1 shows the combined section of the device in side view.

Figure 2 shows a frontal section of the device.

1, 2 should be considered together.

Driven shaft device has the capability of functioning as a drive shaft, so the name of the shafts is conditional.

The device has located coaxially with the driving shaft 1 and driven shaft 2, with the possibility of rotation in bearing sockets motionless body parts (shown conventionally). The shaft 1 is made integral with collapsible hollow cylindrical drum on the inner surface of which is made hinges, pins 3 which perform the function of the cranks of the driving shaft 1.

Inside the drum, with the possibility of the rotation in bearing assemblies, set crankshaft driven shaft 2, is made with three connecting rod necks (or cranks) 4, the two outer cervix which are offset by half a turn relative to the Central neck. The rod shakes 4 mounted for rotation relative to the necks 4 levers - cargo 5 links (also figure 2 - section a-a), a common finger 6 of the hinge arm 7, having a common finger 3 with hinge, made on the inner surface of the drum. In the body of the cargo units 5 is made of profiled grooves 8, which together with the curved shape of the levers 7 allow free rotation of the shafts 1,2 relative to each other without jamming. Center 9 weight each truck element 5 is located in the body of the cargo level 5 outside hinge 6 (common hinge levers). The design of all three cargo units are identical. The mass of the Central freight link 5 is selected equal to the mass amount of external cargo units 5 for static and dynamic balancing device.

In figure 1 above the axis of rotation of the shafts 1, 2 are combined incisions along the symmetry axis of the shaft 2, the axis of symmetry of the outer freight links 5 and 3 fingers. Line of section shown on Figure 2 as a section along B-B. the True position of the journals 4, cargo link 5, the levers 7 and hinges 3 for a freight link is depicted in figure 2.

The finger 3 and the middle hinge freight link in Fig. are before the cut surface and are not visible. The lever 7 average freight link is not shown (deleted).

All nodes of rotation shown conventionally and simply refers to the use of rolling bearings.

Figure 3 shows the kinematic diagram of the device for a freight link.

In a rectangular coordinate system X0Y, we believe that 0 coincides with the axis of rotation of the shafts 1, 2. Then the finger 3 (01) has the ability to move on a circle of radius R1 when the rotation shaft 1.

Crank the neck 4 (center 02) has the ability to move on a circle of radius R2 when the rotation shaft 2. Around, finger 3, assuming its axis of symmetry is also the center of rotation 01 has the possibility of rotation of the lever 7.

Around the crank pin 4, assuming its axis of symmetry also the 02 has the possibility of rotation of the lever 5, which is the freight link, and the finger 6 - General hinge levers will move along the circle of radius R3, and the center of mass 9 of the lever 5 will move along the circle of radius R4.

The lever 7 has a common hinge 6 with the lever 5.

Suppose that the shafts 1, 2 are rotated with a certain constant speed, while

W1>W2, where W1 is the angular velocity of the shaft 1, W2 is the angular velocity of the shaft 2. We will introduce an additional coordinate system X 0Y'rotating relative to the system X0Y with angular velocity W2, in which the center 02 (neck 4 of the shaft 2) is fixed.

Next, see Figure 4.

CE is the Tr masses 9 of the lever 5 for simplicity is not shown.

Take the initial position, when the centers 01 (finger 3) and 02 (neck 4) lie on the axis - H' (minus H'), the centers 01 and 02 will have the maximum convergence, and the levers 5, 7 facing upward.

Assume that the shaft 1 rotates uniformly.

Then after a half-turn of the shaft 1 01 will lie on the axis +H', and the centers 01 and 02 will have the maximum distance, and the levers of 5.7 facing down.

The position of maximum convergence of the cranks (the centers 01 and 02 lie on the axis of minus H') corresponds to the maximum angular speed of the common hinge 6 of the arms 5, 7 with a uniform rotation of the shaft 1.

The position of maximum removal of cranks (centre 02 lies on the axis of the minus H', centre 01 lies on axis +H') meets the minimum angular speed of the common hinge 6 of the arms 5, 7 with a uniform rotation of the shaft 1.

Accordingly, we can identify the phase of the angular acceleration of the common hinge 6 of the arms 5, 7 and the phase of the angular deceleration of the common hinge 6 levers, as well as the points of maximum and minimum speed of the common hinge 6 levers, indicated in figure 4.

It should be noted that whenever the ratio of angular velocities of the shafts 1, 2 within W1>W2 (including W2=0), W1=const, W2=const in the coordinate system X 0Y' phases of acceleration and deceleration of the common hinge 6 of the arms 5, 7 are the same.

The operation of the device is considered for a freight link.

If m is the moment of the load, equal to zero, the center of mass 9 of the lever 5 is most remote from the axis of rotation of the shafts 1, 2 position and the shafts 1, 2 are rotated at the same time. When the load torque is larger than constructively given the transmitted torque drive shaft, the shaft 2 is slowed down, and the lever 5 turns around the neck 4 with periodic acceleration and deceleration of the center of mass 9, passing along the torque of the slave shaft 2. The energy required for acceleration of the center of mass 9 of the lever 5 in the braking process of the center of mass 9 returns the drive shaft 1 through the lever 7 and the finger 3.

When the load torque having a value greater than zero, but less structurally specified torque when the speed of the driving shaft 1, a driven shaft 2 comes into rotation, while W1>W2.

When the crank 3 of the drive shaft moves in a circle, occasionally moving closer and removed from the crank 4 of the driven shaft, resulting in total joint 6 of the arms 5, 7 connecting the cranks 3, 4 has a phase angular acceleration of the hinge 6 and the phase of decreasing angular velocity.

In the phase of the angular acceleration of the hinge 6 (Figure 5), the torque of the driving shaft, is applied through the crank 3 and the lever 7 to the common hinge 6 levers 5,7 accelerates the center of mass 9 of the lever 5, the lever 5 tends to rotate under the action of forces of inertia center of mass 9 and the force arising on the opposite the center of mass 9 side of the lever 5 and the crank is 4 the driven shaft, is directed in the direction of rotation of the crank drive shaft 3.

In the phase of decreasing the angular velocity of the hinge 6 (6) the center of mass 9 of the lever 5, with the excess kinetic energy in the form of the absolute velocity of the center of mass in space gained in the previous phase of acceleration under the action of inertia forces is going to beat slowing the movement of the hinge 6 and rotate the lever 5 around the hinge 6. When this force arising on the opposite from the center of mass 9 side of the lever 5 and the crank 4 of the driven shaft is directed in the same way as in the previous acceleration phase of the common hinge 6 of the levers 5, 7, and the power is transmitted through the lever 7 to the crank drive shaft 3, is directed in the direction of rotation of the drive shaft. As a consequence, the previously accumulated kinetic energy of the center of mass 9 of the lever 5 in the phase of decreasing the angular velocity of the hinge 6 is partially spent on rotation of the crank 4 of the driven shaft, and partially returned through the lever 7 and the crank 3 drive shaft.

Inertial transformer containing the system of coaxially arranged drive and driven shafts and at least one pair of levers having a common pivot and connecting the cranks drive and driven shaft, with one of the levers plays the role of a freight link, characterized in that the lever - freight link is made with penny the ω mass, outside the common hinge levers and mounted on the crank shaft with the possibility of circular rotation locked driven shaft of the device.



 

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