RU2308603C2 - Motion converter - Google Patents

Abstract

FIELD: mechanical engineering, particularly combustion engines, pumps and positive displacement compressors, namely mechanisms, which covert reciprocal movement into rotation and vice versa.

SUBSTANCE: motion converter comprises four cylinders grouped in pairs. Pistons of opposite cylinders are connected with each other through fixed bar. The converter has the first and the second pair of fixedly connected parallel toothed racks brought into engagement with corresponding segmental gear-wheels fixedly connected to one output shaft. In each segmented gear-wheel teeth extend for less than half of 180° pitch circle. Segmented gear-wheels cooperating with corresponding toothed racks are shifted through predetermined angle, preferably 90° angle, one relatively another.

EFFECT: increased performance.

3 cl, 5 dwg, 1 tbl

Description

The invention relates to mechanical engineering, and in particular to mechanisms for converting reciprocating motion into rotational and vice versa, and can be used in internal combustion engines, as well as in pumps and compressors of volume type.

A known mechanism for converting reciprocating motion into rotational and vice versa [1].

This mechanism comprises a housing with a guide mounted in it with the possibility of axial movement of the rod, two cranks and a mechanism for synchronizing their rotation in opposite directions with equal angular velocities, equipped with a link with two slots fixed to the rod, when the longitudinal axis intersects the spikes with rotation axes the latter are located at opposite ends of the wings and installed in its corresponding grooves with the possibility of axial movement, and the plane of rotation of the cranks are mutually parallel.

The disadvantage of this mechanism is the imperfect kinematic scheme, because when converting rotational motion into reciprocating and vice versa in mechanisms with a crank that rotates 360 °, insufficiently complete power take-off occurs, i.e. lower efficiency.

The purpose of the invention is improving efficiency.

Also known "Converter rotational motion in the reciprocating and vice versa" [2], which is taken as a prototype. The prototype contains a housing 1 with gears 2 and 3, performing the function of a synchronization mechanism of rotation in opposite directions with equal angular speeds, mounted on shafts 4 along with wheels 5, on which levers with springs 6 and buffers 7 are mounted on shafts. Shafts 4 with wheels 5 abut against a double-row thrust bearing 8 and angular contact bearings 9, which are mounted in a sleeve 10 with annular grooves into which the crank levers 11 are inserted, pivotally connected to the rods 12 and pistons 13 moving in the cylinder 14, s mounted on the housing and converting the rotational movement of the clutch 15 into the reciprocating motion of the piston 13 or vice versa due to the guide 16 attached to the housing 1 and made with grooves curved in different directions.

When converting rotational motion into reciprocating torque from the electric motor through the clutch 15 is transmitted to the gear 2, which rotates the gears 3 in opposite directions with equal angular speeds. The wheels 3 rotate together with the wheels 5 and the springs 6 with buffers 7, striking the cranks 11, reciprocating pistons and at the same time moving along the guide grooves in the bronze guide 16. In one cycle, the crank 11 passes a certain angle (figure 3) and deviates to the side where the same lever moves it to the other side, making the next beat.

The disadvantage of the prototype is the design complexity and low efficiency associated with a change in the length of the lever in the crank mechanism.

The technical task of this invention is to simplify the design and increase the efficiency of the Converter reciprocating to rotational and rotational and vice versa.

This technical problem is solved as follows.

The motion converter contains four cylinders arranged in pairs, the pistons of mutually opposite cylinders of which are connected to each other motionlessly, through the first and second pair of motionlessly connected parallel gear racks. These racks are in engagement with the respective segment gears. The wheels are mounted motionless on one output shaft. On each gear wheel, the teeth occupy less than half of its pitch circle. In addition, the processes of interaction of the gear racks with the corresponding segment stars are shifted in time in phase, mainly by 90 °.

The shaft in the second embodiment is the drive shaft, and the first and second segment wheels kinematically connected with the corresponding pairs of gear racks are mounted with the possibility of relative displacement along the angle in the range from 0 to ± 180 °, and the reciprocating movement is the output movement.

This converter has a simplified design, low cost, and also increases the service life. Efficiency increases due to the fact that the lever does not change and is equal to the radius of the segmented wheel. Switching the moments of interaction of the gear racks 11-14 with the corresponding segmented gear wheels 16, 19 occurs at the moment when the pistons 5-8 are in dead points. The efficiency of the converter will increase by 43%. With a cosine change in the size of the lever in the crank converter, its average value is 0.57 L _max . In proportion to the length of the lever, the power on the converter shaft will change.

Also known is an internal combustion engine (ICE) [3], which contains a double-acting cylinder and has combined working cavities, and the pistons of adjacent cylinders move in the opposite direction.

In this case, two cylinders 1, 3 are installed only on one side of the shaft parallel to each other in the same cavity (see figure 3). This eliminates the need for two oppositely mounted cylinders 2, 4 and associated rods 9, 10. The gear pairs of the rails 9, 10 and 11, 12 can reciprocate in special guide grooves in the engine housing.

The use of ICE together with the proposed converter will allow you to create a compact engine with high efficiency and low cost.

Figure 1 shows the design of the motion Converter, where:

1, 2, 3, 4 - the first, second, third and fourth cylinders of an internal combustion engine (ICE);

5, 6, 7, 8 - the first, second, third and fourth pistons of the internal combustion engine;

9, 10 - the first and second rods;

11, 12 - the first pair of gear racks;

13, 14 - the second pair of gear racks;

15 - strips;

16 - the first segment gear;

17 - o-rings (not shown);

18 - output shaft.

Figure 2 presents a view of E in figure 1, where the elements 4-18 are the same as in figure 1;

19 - the second segment gear.

20 - a fixing bolt (not shown).

Figure 3 presents a top view of the Converter with parallel installation of the rods, where:

21, 22 - the first and second overrunning clutches;

23 - flywheel;

24 - pinion gear;

25 - transverse trims;

26, 27 - the first and second rods.

Figure 4 presents a view a of figure 3, where:

28 - spring;

29 - swivel joints (not shown).

Figure 5 presents a view In figure 3, where all positions are the same as in figure 3.

Figure 6 presents the second variant of the Converter reciprocating to rotational, where:

30 - racks;

31 - pontoons;

32 - pushers;

33 - chains;

34, 35, 36, 37 - the first, second, third and fourth stars mounted on overrunning clutches;

38, 39 - the first and second shafts;

40, 41 - the first and second gears;

42 - flywheel;

43 - multiplier;

44 - generator;

45 - stand;

46 - guides for pushers.

The principle of operation of the motion Converter, the kinematic diagram of which is presented in figure 1, is as follows.

In the first embodiment of the motion converter, the four cylinders of a four-stroke internal combustion engine 1-4 are mounted crosswise (see figure 1).

The rods 9 of two pistons 5 and 6 (7 and 8) are connected using two parallel bars 15 with the corresponding two parallel gear racks 11 and 12 (13 and 14).

The first pair of gear racks 11 and 12 is engaged with the teeth of the first segment gear 16. The teeth cover only one half of the segment gear. When one of the gear racks 11 or 12 enters the clutch with the teeth of the segment gear 16, the other rack is in the neutral position - out of engagement.

Similarly, a second pair of gear racks 13 and 14, rigidly connected to a second pair of reciprocating pistons 7 and 8, in turn enter into engagement with the teeth of the second segment gear 19.

Since the teeth on the segment gears are located on less than half of the pitch circle, alternate engagement of two parallel gear racks with the gear of the teeth causes the segment gear to rotate in one direction. In figure 1, this interaction of the racks with gear 16 leads to its rotation and the associated shaft 18 counterclockwise.

In segments of the segment gears 16 and 19, where there are no teeth, they are cut off below the level of the hollows between the teeth. The rack in this section does not touch the gear.

To eliminate the “dead point" when the first segment gear 16 is in the neutral position, i.e. out of engagement with both gear racks of the first pair, one of the racks 13 or 14 of the second pair must necessarily be in engagement with the second segment gear 19.

Since the first 16 and second 19 segment gears on the output shaft 18 are fixed, the process of rotation of the shaft is continuous.

The teeth on the first and second segment gears are shifted 180 °, i.e. mutually complement to the full circle. In this case, the racks engage with the gears with a phase shift of 90 °. This corresponds to the fact that when the middle of the first vertical (left) rack 11 is in engagement with the middle teeth of the first segment gear 16, the beginning of the fourth (upper) rack engages with the beginning of the gear half of the second segment gear 19.

Figure 2 shows a view of E of figure 1.

The first 16 and second 19 segment gears are fixedly mounted on the common shaft 18. Since the four cylinders of the four-stroke engine are mounted crosswise, with a shift of 90 ° relative to each other, the phase shift of 90 ° between the processes of interaction of the gear racks 11 and 12 (13 and 14) with the gears 16 (19) is most optimal.

Segment gears are mounted on the cages of overrunning clutches 21, 22, the hubs of which are fixed on the output shaft of the transducer 18. If necessary, a ratchet wheel with a dog can be installed to prevent rotation of the shaft 18 in the opposite direction. To achieve uniform rotation of the electric generator, a massive flywheel 23 can be installed on the shaft 23. Such a motion transducer can be installed to convert wave energy into electrical energy. A drive gear 24 is fixedly mounted on the output shaft of the converter, the rotation of which is transmitted through the multiplier to the generator.

где m - модуль зубца сегментного колеса 16 (19), a R - радиус делительной окружности сегментного колеса. Наиболее оптимальным является сдвиг по фазе 90°.Any other phase shift between the indicated processes and the arrangement of the cylinders is possible. The angle between the axes of the cylinders and the reciprocating directions of the movement of the gear racks can vary from 0 to 360 ° discretely in steps

where m is the tooth modulus of the segmented wheel 16 (19), and R is the radius of the pitch circle of the segmented wheel. The most optimal is a phase shift of 90 °.

The motion Converter, the design of which is shown in figure 3-figure 5, characterized in that all four cylinders 1-4 are installed in the same plane, and the rods 9 and 10 connecting the opposite pairs of pistons 5-6 and 7-8 are parallel to each other friend and are in the plane passing through the axis of the output shaft 18.

Table No. 1 shows the cycle change sequence for a four-stroke ICE during the operation of four I-IV cylinders, where T / 4, T / 2, 3/4 T and T is the sequence of quarter-cycle operation of the cylinders. At each moment of time, one of the cylinders is in the working phase, which ensures uniform rotation of the output shaft of the motion converter.

Table number 1 Suction Compression Explosion Reset T / 4 III IV I II T / 2 II III IV I 3/4 T I II III IV T IV I II III T / 4 III IV I II

In the frontal plane, the angle ϑ between the rods 9 and 10 can vary from 0 to 180 °. In Fig. 1, ϑ = 0 °, and in Fig. 3, ϑ = + 90 °. The phase shift between the moments of interaction of the gear rack pairs 11-14 with the corresponding gear segment gears 16 and 19 is equal to 90 ° regardless of the magnitude and sign of the angle ϑ (see figure 1 and figure 3).

When applying the proposed mechanism for converting rotational motion into reciprocating, if necessary, the angle ϑ can change discretely from 0 to 360 °. The minimum angle is

To do this, it is necessary to change the angular position of one of the segment wheels relative to another, for example, the second wheel 19, by unscrewing the fixing bolt 20 (see figure 2).

At the moment of changing the angular position, the gear 19 should be in engagement with one of the gear racks 13 or 14. Together with the gear 19, all kinematically connected elements must be rotated simultaneously - the gear racks 13, 14; rods 10, pistons 7, 8 and cylinders 3, 4. To do this, all these elements must be installed on a special rotary platform with a lock of its angular position relative to the housing. After turning the platform, the angular position of the segment gear 19 is again fixed by a bolt 20.

The motion Converter shown in figure 1-figure 3, can be used to perform the reverse operation - to convert the rotational motion of the shaft into the reciprocating motion of the gear racks. The need for such a converter arises, for example, to create planing, grinding, saw-cutting machines, etc.

When the shaft 18 and the fixedly connected segment gears 16 and 19 rotate, the gear pairs of the racks 11-12 and 13-14 and the associated rods 9 and 10 make a reciprocating motion.

The principle of operation of the second embodiment of the motion Converter, presented in Fig.6, is as follows.

Two vertical racks 30 are fixedly mounted in the sea. Streamlined pontoons are installed on both sides of each rack. As pontoons can be used catamarans - pedal boats. The weight of the pontoon must be such that it is equal to the weight of the water displaced by the catamaran when it is completely submerged. In this case, the moments of rotation on the shaft created when raising and lowering the pontoons will be equal.

Pontoons are installed so that under the influence of waves they can only oscillate vertically, along the direction of the struts 30. To reduce the pressure in the horizontal direction, catamarans are installed in the direction of the waves.

Vertical pushers 32 are fixedly connected to the pontoons, which, with the help of pushers 46, perform only reciprocating motion in the vertical direction.

In this case, the first and third stars with freewheels 34 and 36 are installed on the first shaft. These stars transmit rotation to the shaft when the pushers 32 raise the chains 33 up. The second 35 and fourth 37 stars rotate the second shaft 39 through the overrunning clutches. This occurs when the pushers 32 and the associated chains 33 are lowered, when the overrunning clutches and the associated stars 35, 37 mounted on the second shaft create a torque on the shaft 39 , the upper stars rotate freely on the first shaft 38.

Thus, when lifting the chains 33, the first shaft rotates, and when they lower, the second shaft.

The reciprocating movement of the pushers 32 and associated circuits 33 is carried out using pontoons 31. Pontoons have positive buoyancy. The weight of the pontoons must be such as to ensure complete immersion. In this case, the moments of rotation created by raising and lowering the pontoons become the same. The shape of the pontoons should be streamlined, like a submarine. As pontoons, you can use catamarans - pedal boats. To prevent rotation of the pontoons around the uprights 30, fixed guides 46 are used, on the first 38 and on the second 39 shafts, the fixed first 40 and second 41 gears are installed. These gears are the same and engage with each other. The decoupling between the rotation of the gears and the rotation of the stars 34-37 is carried out using overrunning clutches. The rotation of the gears occurs in the same direction. A flywheel 42 is installed on the first output shaft 38. The flywheel increases the uniformity of rotation of the output shaft. The rotation of the output shaft through the multiplier 43 is transmitted to the generator 44. The multiplier serves to increase the speed of rotation of the shaft and align it with the speed of rotation of the rotor of the generator. For installation of the multiplier and generator, a fixed stand 45 is used. The proposed transducer of wave energy into electrical energy will solve the problem of coastal protection of the seas.

The proposed motion converter can be used to create a rod-free crank four-stroke internal combustion engine.

Information sources

1. A mechanism for converting reciprocating motion into rotational motion and vice versa. Patent on the application 5008186/28, 09/30/94, bull. Number 18.

2. Ponomarev A.V. Converter of rotational motion to reciprocating and vice versa. RU 2002106181/11, 7 F16H 21/22, Pat. No. 2215919, Bull. No. 31, 2003.

3. Chopovsky B. P., Kozulin V. B. Internal combustion engine. RU 2002126052/06, 7 F02B 33/00, 09/30/2002.

Claims (3)

1. The motion Converter containing four cylinders arranged in pairs, the pistons of mutually opposite cylinders of which are connected to each other by a rod motionless, characterized in that it contains the first and second pair of motionlessly connected parallel gear racks that are engaged with the corresponding segment gears mounted motionless on one output shaft, while in each segment gear the teeth occupy less than half of the pitch circle by 180 °, and the segment gears interacting with the corresponding stvuyuschimi toothed racks are offset from each other by a certain angle, preferably 90 °. 2. The motion Converter according to claim 1, characterized in that the shaft is driving, and the first and second segment gears kinematically connected with the corresponding pairs of gear racks are mounted with the possibility of relative displacement in the angle from 0 to 180 °, and their return - translational motion is the output motion. 3. The motion Converter according to claim 1, characterized in that each rod is connected to the midpoints of two transverse parallel slats, the ends of which are also connected to the ends of the respective parallel gear rails, forming a rectangle, the two opposite corners of which interact with a spring-loaded pusher mounted on the corresponding segment gear.

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