EA003724B1 - Conversion of rectilinear reciprocating motion into rotational motion - Google Patents

Abstract

1. A device for converting a rotational motion into a rectilinear reciprocating motion, and vice versa, in particular for the use in volumetric internal combustion engines, and in compressors, characterized in that it comprises: only one auxiliary crank (4) and only one rotor (30) containing the axis of rotation of the auxiliary crank (4), which are both arranged on only one side of the auxiliary crank pin (15); means (1, 3) which impose to the auxiliary crank (4) and to the rotor (30) rotational motions such that when the auxiliary crank (4) performs a rotation in one direction, said rotor (30) rotates by half that angle and in the opposite direction; said means (1, 3) comprising a planet wheel (3) integral with said auxiliary crank (4) and which is located between two supports arranged inside the rotor (30), and a ring gear (1) with internal toothing, integral with a housing (7); said rotor (30) being monolithic and located inside the housing (7); the pitch circle diameter of the planet wheel (3) being equal to half the pitch circle diameter of the ring gear with internal toothing; and the input or drawing of power being performed by means of a shaft (16) which is integral with the rotor (30) and rotates with it. 2. A device according to claim 1, wherein the device can be used for the construction of machines comprising several devices of the same kind, which are synchronised with respect to each other by means of a shaft simultaneously engaging the rotor (30) of each of said devices; the axis of said shaft being arranged so as to not hinder the rectilinear reciprocating motions of the connecting rod pin (15) of each device. 3. A device according to claim 2, wherein said shaft, besides performing the synchronisation of the various devices, also collects the torque of each device, and outputs them at a single power take-off.

Description

Technical field

The present invention relates to a device that can be used instead of the classic crank mechanism to convert a reciprocating linear motion into rotational motion and vice versa.

More precisely, the proposed device can be applied to a volumetric internal combustion engine with reciprocating motion or to a compressor, although it is not limited to such an application.

Background to the invention

The conventional crank mechanism of an internal combustion engine has several drawbacks.

One of these drawbacks is the frictional force, briefly denoted by Na, which acts between the side surface of the piston and the cylinder wall during the sliding movement of the piston and which arises from a reaction to the pushing action of the connecting rod.

This leads to the fact that in all types of volumetric engines with reciprocating motion there is a significant drop in efficiency caused by energy dissipation due to the mentioned force, especially in two-stroke (two-stroke) engines, in which case a large amount of oil is used in gasoline (2%), in order to ensure a satisfactory working process and satisfactory glide, while the combustion of gasoline leads to a high level of pollution.

Another disadvantage is the tipping force with which the connecting rod acts on the piston, which leads to the requirement that the piston has a length that avoids jamming. However, the increased size leads to increased weight and, consequently, to an increase in inertia, as a result of which the efficiency is reduced.

A noticeable lightening of the components of the mechanism, together with an increased efficiency of cooling the cylinder, could be achieved if a certain working volume could be obtained using small cylinder bores and large stroke lengths. In this regard, the classic crank mechanism has certain limits, since it usually contains a connecting rod, which during its movement simultaneously performs translational movement and oscillation, thereby preventing its passage beyond certain limits of travel due to problems associated with space (obstacle).

An object of the present invention is to provide a device suitable for converting rectilinear reciprocating motion into rotational motion and vice versa based on a completely different principle, according to which the end of the auxiliary crank will move in a straight line instead of performing a rotational motion.

Another objective of the invention, if applied to an internal combustion engine, is to provide a device that eliminates the aforementioned disadvantages inherent in known technical solutions.

In particular, the device will provide a more efficient transmission by the piston to the drive shaft of the force generated inside the combustion chamber by obtaining, during each cycle, a diagram of the engine torque, which is much more preferable. Since the engine power at each moment of time is a product of angular velocity and torque, it can be established that the total power will be increased.

An additional object of the present invention is to use elements or components that perform a rotational movement and are naturally balanced due to their shape to create a device for converting linear reciprocating motion into rotational motion. Therefore, they do not require additional balances. Even if rotation occurs at a very high rpm, the vibrations of the drive shaft are greatly reduced and the movement will be very smooth.

Disclosure of invention

The aforementioned tasks set in the present invention are solved by means of a device for converting rectilinear reciprocating motion into rotational motion or vice versa, containing only one auxiliary crank (4) and only one rotor (30) containing the axis of rotation of the auxiliary crank (4), both of which are located on only one side of the finger (15) of the auxiliary crank;

means (1, 3) that impart rotational movement to the auxiliary crank (4) and rotor (30) such that when the auxiliary crank (4) rotates in one direction, the rotor (30) rotates half this angle, but in opposite direction;

wherein said means (1, 3) contain a planetary gear (3), which is made integrally with an auxiliary crank (4) and which is located between two bearings located on the inside of the rotor (30), as well as gear (1) with internal gearing, which is made integral with the housing (7); the rotor (30) is made integral and located inside the housing (7);

moreover, the diameter of the pitch circle of the planetary gear (3) is equal to half the diameter of the pitch circle of the gear (1) with internal gearing;

power supply or power take-off is carried out by means of a shaft (16), which is made integrally with the rotor (30) and rotates with it.

When applied to internal combustion engines, the auxiliary crank pin is connected to the cylinder piston by means of a rod or rod. The auxiliary crank finger will make a rectilinear or almost rectilinear reciprocating motion. In the case of rectilinear movement, the rod or rod need not be connected to the piston by means of a swivel joint and can be rigidly connected to it.

Therefore, said rod or rod intended to be connected to the movable element can also be called a plunger.

In the case of internal combustion engines, the movable element is a piston, which performs a reciprocating linear motion. Obviously, this implies that the stroke of the piston can be significantly larger than its diameter. This allows you to choose (choose) the size of the components of the device depending on the force acting on the piston, which will be less if the working volumes are determined by small cylinder bores and long strokes. Thus, the weight of the engine will be reduced. Said means for communicating to the auxiliary crank and rotor the aforementioned relative motions are preferably in the form of gear wheels.

According to claim 1, by installing an auxiliary crank on the ring gear, when the diameter of the pitch circle of the ring gear or planetary gear is equal to half the diameter of the pitch circle of the twin gear (gears with internal gearing), it is possible to rotate the ring or planetary gear angle 2a around its axis . At the same time, the rotor and the center of the planetary gear (or the center of the auxiliary crank) will be moved an angle a in the opposite direction around the center of the rotor, the latter being a rotational element, which, for example, (if applied to internal combustion engines) is connected directly or indirectly to the drive shaft of the engine.

The effect that is achieved and which is the real goal of the invention is that the auxiliary crank pin will move along an almost straight path, while the said path is a completely straight path, provided that the centers of two hook gears (planetary gear and twin gears or gears with internal gearing) define a segment equal to the radius of the orbit of the center of rotation of the planetary gear, which exactly corresponds to the distance between the finger auxiliary th crank and the center of the planetary gear (crown gear).

It is of paramount importance that the diameter of the gear cutting of the twin gear (pitch diameter) is always equal to twice the diameter of the planet gear (the gear ring of the planet gear).

According to claim 2, several devices of the same type, designed in accordance with the idea of the present invention, can be used to create a machine in which power is removed (collected) by means of a single drive shaft, which simultaneously engages with different rotors of the devices .

The present invention and some of its advantages will be better understood when considering the following detailed description of a preferred embodiment of the invention.

Brief Description of the Drawings

Hereinafter, the present invention will be described for illustrative purposes without imposing any restrictions with reference to a preferred embodiment of the structure shown in the figures in which in FIG. 1 schematically shows only the principle of operation of the device according to the present invention, which is itself known, in comparison with the classical crank mechanism;

in FIG. 2 is a view of a node formed by an internal gear or a pair of gears, a planetary gear, which is integral with the auxiliary crank, and the auxiliary crank itself in the position corresponding to the top dead center (TDC) of the movable element reciprocating in rectilinear motion, moreover, this figure shows the use of two gear wheels to implement the device;

in FIG. 3 is a view of the assembly shown in FIG. 2, showing, in an intermediate position of the planetary gear, operating conditions regarding relative rotation angles that can be considered satisfactory, and how the finger of the auxiliary crank moves in a straight line (X axis);

in FIG. 4 shows a sequence of movements of a planetary gear (ring gear) according to four different positions;

in FIG. 5 shows a case of use, according to which instead of an auxiliary crank, a disk is used in order to provide a large number of fingers on it, the geometrical places of the points of which correspond to reciprocating rectilinear paths that do not coincide in phase with respect to each other;

In FIG. 6 is a view of a preferred embodiment of a device of the present invention.

Preferred option

The principle on which the invention is based and which is known per se is to divide the shoulder of the classic crank mechanism into two articulated (articulated) parts and to inform them during the movement of the opposite rotation so that one revolution of one part corresponds to two turns of the other parts.

In order to better explain this principle, in FIG. 1, the classical reciprocating volumetric engine system, composed by a connecting rod and crank, is depicted on the left side of the figure in the TDC position (top dead center) and, accordingly, in a characteristic position, while the same engine is presented on the right side, but with the crank, divided into two parts, corresponding to the segments OS and CB, pivotally connected to each other at point C, while the segment CB is forcibly rotated around the hinge C by angles that are twice as many as the angles covered by a sharp OS during movement in the opposite direction.

In both figures, the center O represents the axis of the drive shaft (or, rather, the intersection of this axis with the plane of the figure).

We consider each case of a characteristic position following the TDC position shown at the top of FIG. 1. In the classical crank mechanism, the finger B of the crank at a certain offset to the piston will be moved at an angle a along a circular path ΐ with a radius of OB. In the device according to the invention, during the same offset to the piston, the segment of the OS will rotate clockwise (counterclockwise) about the axis O by angle b, and the segment BC will rotate counterclockwise (clockwise) around the joint C.

This relative motion creates the trajectory of point B, which is, in general, almost straight with a slight bulge to the right or left with respect to the axis X-X of the piston, depending on whether the length of the segment of the aircraft is longer or shorter than the segment of the OS (in Fig. 1 BC more than the OS and the trajectory has a bulge to the right, as shown).

Obviously, if OS = CB, then the trajectory of point B will be completely rectilinear and will go through the center of O.

To implement this principle, gear wheels can be applied, which, through their gear ratios, allow the connection to be realized during the movement, according to which, when the segment of the OS makes an angle b around the center О, the segment CB makes an angle that is twice as much as the mentioned angle, but in the opposite direction of rotation.

For this purpose, use a pair of gears or gear 1 with internal gearing 2 and a planetary gear or crown gear 3 (see Fig. 2), which are configured so that the diameter of the pitch circle of the first of the mentioned gears is twice the diameter of the pitch circle of the last gear.

In FIG. 2 schematically shows an arrangement of basic elements or components whose relative motion is used to provide the desired reciprocating motion. In this figure, compared with the right side of FIG. 1 it can be seen that the center O1 of the gear 1 with internal gearing corresponds to the point O, the center O2 of the planetary gear 3 corresponds to the point C and, finally, that the auxiliary crank 4, made as a whole with the planetary gear, is schematically represented as a segment CB; its point O3 corresponds to point B and covers point T, that is, it coincides with this point, where the two pitch circles of gears 2, 5 are tangential to each other at top dead center (TDC). Now imagine that we are forcing the segment O1-O2 to make a right-handed turn (clockwise) by a characteristic angle a around the center O1 and that the position of the gear 1 with internal gear is always in the same plane, as shown in FIG. 3.

The planetary gear 3, which engages with the gear 1 with internal teeth, will also rotate around its axis O2 due to the rotation of its center O2 around O1, and the said rotation of the planetary gear corresponds to the angle 2a (since the gear ratio between these two elements is 2: 1) and will occur in the opposite direction (counterclockwise).

The auxiliary crank 4, which, as mentioned above, is made integrally with the planetary gear 3, will rotate by the same angle as the last, thereby shifting its point O3 again along the X axis according to FIG. 2.

In FIG. Figure 4 presents some of the indefinite number of positions that the system can occupy during rotation in order to better illustrate the dynamics of movement, moreover, this figure also shows two points 8 and I, which correspond to the end positions of the stroke.

It is interesting to note that if the disk 6, which is also made integrally with the planetary gear, is used instead of the auxiliary crank 4 according to FIG. 2, as shown in FIG. 5, by fixing on the disk the characteristic point 04, rotated by a certain angle 2a with respect to 02 and located on the same circle as 03, the said point during rotation will move along a different rectilinear path that is deflected by an angle a with respect to to the first trajectory (X axis).

In conclusion, we can say that a large number of moving elements with rectilinear reciprocating motion, which do not coincide with each other in phase at an arbitrary angle, can be connected to the disk 6 and around it.

Here, for clarity, in accordance with the function performed, it is advisable to define segment AB as a plunger (Fig. 1), as an auxiliary crank segment BC and as a rotor, a cylinder whose axis passes through O and includes an axis intersecting the figure plane at point C.

In FIG. 6 is a cross-sectional view of a preferred embodiment of a device structure.

According to FIG. 6, gear 1 with internal gearing goes inside the block or frame 7, equipped with a cover 8.

A planetary gear 3 with a radius of I / 2 is actually introduced from the inside of the rotor 30, while the latter is provided with a cylindrical seat 9. The ring gear of the planetary gear 3, indicated by 5, is engaged with a pair of gears or with gear 1 having an internal gear cutting with a double radius (equal to I) with respect to the radius of the planetary gear 3.

In FIG. 6, in particular, it can be seen that the cylindrical seat 9 has a gap, that is, it does not extend along the entire longitudinal extent of the rotor 30, so that the ring gear 5 of the planetary gear 3 can engage with a twin gear or with gear 1 having an internal gear cutting, which is indicated by 2.

In FIG. 6, it can also be noted that the planetary gear 3 with radius I / 2 has a hub 11 made integral with it, located on the inside of the extension of the rotor 30.

The hub 11 goes inside the bearings or bearing shells (shaded part).

In addition, the planetary gear 3 and the rotor 30 are held by bearings or a bearing shell, respectively, indicated at 12 and 13.

The part of the rotor 30, indicated by 10 and located close to the wall 8, can form a gear. The gear 10 can remain unclosed (the upper wall 7 according to Fig. 6 is not made) and can be used to synchronize several devices of the same type by means of a synchronizing shaft (not shown), which selects and stores the power of a large number of devices.

In FIG. 6, the drive shaft is indicated by 16 and is made integrally with the rotor 30; it protrudes from the wall 8. It can also be seen that the drive shaft 16 is held by the bearing shell 17.

From FIG. 6 it is obvious that the axis 18, 19, 20 respectively denote the axis of the components 16, 3, 15.

It is advisable to recall and emphasize that in the case when more than one mechanism is assembled in the same engine, it is necessary to ensure the synchronization of these mechanisms.

This can be achieved as follows:

gear 10 is rigidly fixed, for example, with a key or directly formed on each rotor 30, while each of the mentioned gears has the same pitch circle diameter as other gears (see, for example, in Fig. 6, the area between gear 1 and cover 8; part 10 of rotor 30);

a transverse shaft is added to the assembly, which has a certain number of gears corresponding to the number of devices (mechanisms), with each of the gears of the transverse shaft engaging with the corresponding gear 10.

Naturally, since the additional shaft, in addition to the synchronization function, also solves the problem of perceiving the work performed by each mechanism, it will provide a single power take-off from the engine or machine at the outlet of its housing.

Industrial applicability

Some goals, which are completely impossible to achieve through a traditional system consisting of a crank and a connecting rod, can be achieved through a new cantilever device, which is designed to convert rectilinear reciprocating motion into rotational motion.

In short, some of these goals are as follows:

in increasing the value of Nm (engine torque);

in the complete exclusion of the traditional force (P! a), which is the friction force, which is one of the most harmful forces acting against movement, and which affects the piston’s sliding movement between its lateral surface and the cylinder wall due to the reaction to the pushing action, created by the crank. A direct consequence of this fact is a significant reduction in the amount of oil used to lubricate the walls;

the possibility of using large displacement volumes and small bore diameters of the cylinders without the need for an excessive increase in engine volume. Thus, very large values of the strokes can be provided and, therefore, very long lateral surfaces of the cylinders interconnected with such strokes, thereby allowing a much more efficient dissipation of the generated heat;

in a noticeable reduction in the weight of the components of the device (a direct consequence of what is indicated in the previous paragraph);

in obtaining a device whose components or elements that rotate can be naturally balanced due to their shape. Therefore, when using these components in this system, there is no need to use counterweights.

Practical tests have shown that for the same constant working volume compared with traditional engines, you can get higher power and more even (correct) rotation of the drive shaft with a significant reduction in vibration.

Finally, it is possible to rigidly connect the piston located at the end of the plunger (segment AB in Fig. 1) with the plunger itself without the need for using any hinge, while the piston can have a minimum longitudinal dimension that is sufficient only to install the piston rings.

Claims (3)

CLAIM 1. A device for converting rotational motion into rectilinear reciprocating motion and vice versa, in particular, for use in volumetric internal combustion engines and compressors, and it contains only one auxiliary crank (4) and only one rotor (30) containing the axis of rotation of the auxiliary crank (4), both of which are located on only one side of the finger (15) of the auxiliary crank; means (1, 3) that impart rotational movement to the auxiliary crank (4) and rotor (30) such that when the auxiliary crank (4) rotates in one direction, the rotor (30) rotates half this angle in the opposite direction ; wherein said means (1, 3) comprise a planetary gear (3), which is made integrally with the auxiliary crank (4) and which is located between two bearings located on the inside of the rotor (30), and the gear (1) with the inside gearing, made as a whole with the body (7); the rotor (30) is made integral and located inside the housing (7); moreover, the diameter of the pitch circle of the planetary gear (3) is equal to half the diameter of the gear (1) with internal gearing; the supply or power take-off is carried out by means of a shaft (16), which is made integrally with the rotor (30) and rotates with it. 2. The device according to claim 1, in which the device can be used to construct machines containing several devices of the same type, which are synchronized relative to each other by means of a shaft that is simultaneously engaged with the rotor (30) of each of the said devices; the axis of the said shaft is positioned so that it does not interfere with the rectilinear reciprocating movement of the finger (15) of the auxiliary crank (4) of each device. 3. The device according to claim 2, in which the said shafts, in addition to synchronizing various devices, also accumulate the torque of each device and issue them from one power take-off.