LV13238B - Mechanical device for distribution of gases that automatically changes phases of intake/exhaust depending of workload and speed of engine - Google Patents

Abstract

The invention refers to the mechanical engineering industry, more properly - to the internal combustion engine gas-distributing device configuration improvement. In the proposed device for the internal combustion engine the injecting and exhausting gas valve timing occurs in automatic mode in relation to the load applied to the engine shaft and the shaft speed. Several alternatives of the invention realization are proposed. In the first variant the gas-distributing device (fig. 4) is made as the four helical gears 19, 20, 25 and 27 permanent coupling, where the gears 19 and 20 teeth spiral direction is opposite to the teeth spiral direction of the gears 25 and 27, at that the weight 17 centrifugal force compressing the governor spring 24 and the slide bushing 28 slipping along the gear 22, cause the gears 19 and 25 axial displacement, which result in the gears 20 and 27 opposite pivoting, which, in their turn, pivot the camshafts 21 and 26 in opposite directions, thus causing more wide admission and emission valve timing. In the second variant of the invention realization (fig. 5), as against to the fig. 4, the gears 19 and 25 are substituted with one gear 29, which a part 19' of the teeth spiral is similar to the gear 19 teeth spiral, but the second part 25' - is similar to the gear 25 teeth spiral. In the both variants the camshafts cams are in the direct interaction with admission 10 and emission 11 valves. Therefore on both sides of each cylinder flow head it is necessary to place one intake and one discharge manifolds, attached to the relative admission 9 and emission 12 ducts. In the third variant of the invention realization (fig. 3) the camshafts cams 30 and 31 operates through the rocker arms 33, mounted on the axle 32, at that each cylinder has four distributing valves - two admission 10 and two emission 11 valves are disposed in mutually antithetic position, as well as two camshafts 21 and 26, which are similar by construction with those installed in the two camshafts engines - each cylinder has one admission and one emission camshaft. In such a rocker arms 33 and cams 30 and 31 interaction with admission 10 and emission 11 valves it is necessary to have one intake and one discharge manifold, installed on the cylinder flow head opposite sides.

Description

Mechanical gas-distribution device which automatically changes the inlet and exhaust gas distribution phases according to engine load and speed

Description of the Invention

The invention relates to mechanical engineering, and more particularly to the design of a gas distribution mechanism for an internal combustion engine. A device is provided for the mechanical-automatic control of the change of the inlet and exhaust gas distribution phases of an internal combustion engine depending on the load applied to the engine and the speed.

The function of the gas distribution mechanism is to inject combustion mixture or air into the engine cylinders in a timely manner and to remove combustion products. Depending on the number of cylinders of the engine, the number of liters or the type of application, the construction and the parameters of these mechanisms vary. Valve mechanisms are most commonly used in motorcycle engines, which provide full gas exchange at high speed, at which maximum power is achieved.

The inlet and outlet process are the result of the combined operation of the valves, their drive mechanism and the camshaft. The efficiency of the gas-distribution mechanism of a multi-cylinder engine shall be assessed by the factor of filling and the uniformity of filling of the individual cylinders. The inlet and outlet valves are opened and closed before or after the piston changeover points for better cylinder filling and exhaust bleeding. The degree of opening and closing of the valves is determined by the angle of rotation of the crankshaft.

The maximum values of the valve lift and blow-through area, as well as the distribution phases, do not fully describe the valve's throughput and gas distribution mechanism work as a whole. For this purpose, a parameter time slot is selected which describes both the valve flowrate and the flowrate.

Commonly known gas distribution mechanisms for internal combustion engines are shown in Fig. 1, wherein: a, b, c, and d mechanisms are provided with an upper camshaft drive and valve arrangement at the cylinder head; e - mechanism with upper valves and lower camshaft; f - mechanism with bottom valves. Fig. 1 uses the following designations: 1 - camshaft with cams; 2 - valve; 3 - spring; 4, 5, 6 traverse; 7 - sliding bar; 8 - Cylindrical slider.

There is known a gas distribution device (Fig. 2a) having four gas distribution valves per cylinder, with two distribution shafts located on the cylinder head. One camshaft is designed to simultaneously open and close both inlet valves 10, both located on the same side of the combustion chamber 14, through two inlets 9 at a time. With the known device, which is located on the front of the inlet camshaft with the drive gear, as the engine speed increases, both inlet valves 10 are opened and closed simultaneously faster.

The objects of the invention are:

- reduce the idling speed at which the engine operates without vibration;

- to prevent engine hanging, which is typical of internal combustion engines at low revs from 0 to 1200 min '¹;

- to achieve maximum engine power not only at high speed but also to achieve the maximum power corresponding to each phase of the gas distribution phase;

- to achieve a better mixing of air and fuel, leading to more complete combustion of the mixture, fuel economy and reduced atmospheric pollution.

The stated aim is achieved by replacing known gas distribution devices with a gas distribution mechanism which automatically changes the intake and exhaust gas distribution phases depending on the engine load and speed, whereby:

the inlet 9 and exhaust 12 channels and the inlet 10 and exhaust 11 valves are co-located at the engine head;

- a transmission from the crankshaft to the gear 23 for realizing the regulator shaft 15, the gear 22 and the sliding sleeve 28 having a cross 18 and a gear 19 and 25 with oppositely inclined teeth;

- the pinion 19 rotates the pinion 20 and the camshaft 21, while the pinion 25 rotates the pinion 27 and the camshaft 26;

- 19 and 20 gear incline is opposite to gear 25 and 27 gear.

The following drawings illustrate the invention:

Fig. 2b shows the arrangement of inlet 9 and outlet 12 channels and inlet 10 and outlet 11 valves per cylinder and gas flow directions according to the invention in order to implement a mechanically automated gas phase distribution;

Fig. 3 shows the position of the levers 33 on the shaft 32 as well as the position of the inlet 30 and outlet 31 cams on the camshaft and their operation relative to the inlet 10 and outlet 11;

Figures 4 and 5 show two embodiments of the proposed device kinematic scheme;

- Fig. 6a, b, c, d show the variation of the inlet and exhaust gas distribution phases of the proposed device during engine operation as a function of engine load and speed: a at idle, b - engine at low speed, c - engine at idle at high speeds, the d - engine working at very high speeds.

In the above drawings the following symbols are used: 9 - inlet channel; 10 - inlet valve; 11 - Exhaust valve; 12 - exhaust channel; 13 - fuel or electric spark supply port; 14 combustion chamber; 15 - regulator drive shaft; 16 - barrier plate; 17 - counterweight; 18 crosses; 19 - cross gear with teeth inclined to one side; 20 - a gear which pairs with a gear 19; 21 - Camshaft left; 22 - regulator drive shaft gear; 23 - driven gear which is driven from the crankshaft; 24 - spring; 25 - cogwheel gear with teeth inclined to the other side than gear 19; 26 - right camshaft; 27 - a gear that works with a gear 25; 28 - Slide sleeve with internal gear teeth; 29 is a cross-geared toothed tooth which, in the embodiment of the invention illustrated in Fig. 5, combines the gears 19 and 25; 30 - the camshaft cam, which opens and closes the inlet valve; 31 - camshaft cam, which opens and closes the exhaust valve; 32 - axis; 33 - levers located on the axle.

Detailed Description of the Invention

The propeller 23 of the proposed gas distribution mechanism regulator (Figs. 4 and 5) is driven from the crankshaft. The gear 20 and the camshaft 21 as well as the gear 27 and the camshaft 26 rotate in the opposite direction of rotation of the regulator shaft 15. The pinion 23 rotates the pinion 22 through the shaft 15, which is in constant engagement with the pinion-type slider 28. The pinions 19 and 25 are spaced apart from each other and with the ratchet 18 are able to move along the pinion 22 in axial direction depending on the position of the weights. At low engine speeds the centrifugal force of the weights 17 is low, therefore the gas distribution phases correspond to the position of Fig. 6a.

As the revolutions increase, the centrifugal force of the weights 17 increases, and by overcoming the spring force of the spring 24, the gears 19 and 25 are axially displaced, which in turn, by means of slanting gear and 26. This is because, as the sleeve 28 slides with the internal toothed gear along the gear 22, the gear 20 and the camshaft 21 are rotated in an additional direction of rotation and the gear 2J is rotated by the gear 25 against the rotation direction of the gear 20 and camshaft . As a result of the operation of the gears 19, 20, 25 and 27, the camshafts 21 and 26 of the camshafts are deflected in opposite directions, resulting in wider inlet and exhaust gas distribution phases. The gas distribution phases in this case correspond to the state of Fig. 6b. With further increases in revolutions, the gas distribution phases correspond to Figs. 6c and 6d.

Conversely, in the overload mode, the speed of rotation and the centrifugal force of the weights 17 are reduced. The force of the springs 24 causes the camshafts 21 and 26 to shift diametrically back through their gears 19 and 25 to their original position, and a gradual transition of the gas distribution phases from the position of Fig.6d to the lower c- and then to the lower b- and for a-states. When the engine is stopped, the regulator returns the gas distribution phases to the starting position (set state).

Depending on the application of the gas distributor offered, eg in street or sports cars, the ratio of gear ratio to gear ratio i to gear ratio 23 should be chosen i = 1: 1 and 1: 2 respectively.

-3Engineers for urban use would prefer the gradual transition from position shown in Fig.6a to position b, and for sports cars the transition from position b to c and further to position d for extreme mode machines and even higher. To take advantage of these benefits and to save fuel, you need to choose a suitable gearbox with better gear ratios as well as other size tires.

In the first embodiment of the invention (see FIG. 4 and formula points 1-4), the kinematic diagram of the gas distribution phase regulator construction (FIG. 4) is designed as a permanent connection of four gear teeth 19, 20, 25 and 27, The 19 and 20 tooth pitch is the opposite of the 25 and 27 tooth pitch. The centrifugal force of the weights 17 compresses the regulator spring 24 and, by sliding the sleeve 28 along the gear 22, causes the gears 19 and 25 to axially rotate each of the gears 20 and 27 diametrically opposite to each other by turning the camshafts 21 and 26. creating wider inlet and exhaust gas distribution phases.

In the second embodiment of the invention (see FIG. 5 and formula points 5 to 8), the gears 19 and 25 are replaced by a single gear 29 with a tooth pitch 19 'similar to that of the gear 19 in comparison with FIG. tooth pitch, but the second part 25 'is analogous to rack 25 pitch.

In both embodiments of the invention described above, the inlet valves 10 and the outlet valves 11 of the engine combustion chamber are arranged in the order shown in Fig. 2b. Two camshafts 21 and 26 are used, which are similar in design to those mounted on two-valve engine motors, one per inlet and outlet valve per cylinder. This arrangement of the valves (Fig. 2b) creates a vortex flow at the inlet, which contributes to a better combustion formation and combustion process. Conversely, a higher quality exhaust is achieved with the opening of the exhaust valves.

In a third embodiment of the invention (see FIG. 3 and Claim 9 of the formula), the gas distribution regulator mechanism (FIG. 4 or FIG. 5) is also employed in the operation of the gas distribution mechanism. The camshafts 21 and 26 are provided with inlet 30 and outlet 31 cams, which actuate the inlet 10 and outlet 11 by means of axis 32 and levers 33. When the engine reaches a certain speed, the camshafts 21 and 26 are rotated diametrically opposite to each other. As a result, the intake manifold 30 acts on one of the inlet valves 10 through the lever 33 on the shaft 32 to the other inlet valve. the valve 10 is actuated through the lever 33 by an inlet cam 30 located on the second camshaft 26, which is rotated by the regulators (FIG. 4 or FIG. 5) in the opposite direction to the camshaft 21. The inlet cups 30 are deflected in opposite directions, resulting in wider inlet gas distribution phases. The exhaust cam 31 of the camshaft 26 acts on one of the exhaust valves 11 through the lever 33 and the other outlet valve 11 through the lever 33 located on the shaft 32 is actuated by the cam 31 on the camshaft 21. The reducer (FIG. or FIG. 5) is rotated to opposite sides of the camshafts 21 and 26. This results in a deflection of the exhaust cams 31 in opposite directions, resulting in wider exhaust phases.

Advantages of the offered gas distribution device:

- the device may be constructed on the basis of existing gas distribution device components;

- it is possible to reduce the idling speed of the engine to 400 and below, at which the engine operates without vibration;

- reduced fuel consumption and atmospheric pollution in urban mobility;

- Better gas exchange at different engine speeds, increased engine power and improved dynamics.

Used information sources:

1. Construction of tractors and automobile engines. Theory and Calculation (Edited by Furoka and G. Melgalvis), Riga, Star, 1980

2. / (BnraTejin BHyTpeHHoro cropaHHH. ΥετροίΐϋΤΒΟ h pa6oTa nopiUHeBbix h KOM6nHnpoBaHHbix aBHraTejiefi (noa peaaKUHeii A.C. OpariHa.

-43. Μ. Α. MacHHO, Β. Η. AjieKceee, Γ. Β. Motobhjihh. Αβτομο6μπι> ημ6 MaTepnajībi. CnpaeoHHHK HHTKeHepa MexaHHKa. MocKBa, TpaHcnopT, 1979.r.

Claims (8)

Formula of the Invention A gas distributor (Fig. 4) which automatically changes the inlet and exhaust gas distribution phases according to the load applied to the engine and the rotational speed, characterized in that it is formed as a permanent connection of four pinions 19, 20, 25 and 27, wherein the ramps of the gears 19 and 20 are formed opposite to the rack of the gears 25 and 27, whereby the centrifugal force of the weights 17 which presses the regulator spring 24 while the sleeve 28 slides over the gear 22 causes axial movement of the gears 19 and 25 rotates its gears 20 and 27 and rotates camshafts 21 and 26 to opposite sides, thereby generating wider inlet and exhaust manifold phases. A gas dispenser according to claim 1, wherein the pinion 19 rotates the pinion 20 and the camshaft 21 and the pinion 25 rotates the pinion 27 and the camshaft 26. A gas dispenser according to claim 1 or 2, wherein the power transmission from the crankshaft to the gearwheel 23 is carried out by the regulating shaft 15, the gearwheel 22 and the sliding sleeve 28 incorporating a cross 18 and gears 19 and 25 with oppositely inclined teeth. A gas distribution device according to any one of the preceding claims, wherein the inlet 9 and the outlet 12 channels and the inlet 10 and exhaust 11 valves are jointly located in the engine head, each cylinder having four gas distribution valves arranged crosswise (fig.2b) - two inlet 10 and two outlet 11 valves - and two gas camshafts 21 and 26, resulting in the camshaft cams in direct contact with the inlet 10 and exhaust 11 cams and at this interaction between the camshaft cams and shafts on each side of each cylinder head one inlet and outlet manifold mounted on respective inlet 9 and outlet 12 channels. 5. A gas distributor (Fig. 5) which automatically changes the inlet and exhaust gas distribution phases according to the load applied to the engine and the rotational speed, characterized in that it is formed as a permanent connection of three gears 20, 27 and 29, where The gears 19 and 25 described in (1) are replaced by one gear 29 having a tooth pitch 19 'in one portion analogous to that of a tooth 19 and the other portion 25' being similar to a tooth 25 having an opposite pitch to the gears 19 'and 20 The centrifugal force of the 25 'and 27 gears tooth pitch and the weights 17 which compresses the regulator spring 24 as the sleeve 28 slides along the gear 22 causes axial movement of the gears 19' and 25 'which rotates each of the gears 20 and 27 diametrically opposite to each other. on the opposite sides also the camshafts 21 and 26 and thus create wider inlet and exhaust gas distribution phases. A gas dispenser according to claim 5, wherein the pinion 19 'rotates the pinion 20 and the camshaft 21 and the pinion 25' rotates the pinion 27 and the camshaft 26. 7. A gas dispenser according to claim 5 or 6, wherein the power transmission from the crankshaft to the gear 23 is provided by the regulating shaft 15, the gear 22 and the sliding sleeve 28 incorporating a cross 18 and gears 19 'and 25' with oppositely inclined teeth. A gas distribution device according to any one of claims 5 to 7, wherein the inlet 9 and outlet 12 channels and the inlet 10 and outlet 11 valves are co-located at the head of the engine, each cylinder having four gas distribution valves arranged in a crosswise direction. 2b) two inlet 10 and two outlet 11 valves - and two gas camshafts 21 and 26, resulting in the gas camshaft bumps being in direct contact with the inlet 10 and exhaust 11 cams and at each cylinder interaction between such camshafts with one inlet and outlet manifold mounted on respective inlet 9 and outlet 12 channels on each side of the head. -59. A gas distributor which automatically changes the inlet and exhaust gas distribution phases according to the load applied to the engine and the rotational speed, characterized in that the camshaft cams 30 and 31 operate via levers 33 which placed on the shaft 32, each cylinder having four camshafts - two inlet valves 10 and two exhaust valves 11 opposite each other - and two camshafts 21 and 26, which are similar in design to those mounted on two-valve engines - one inlet and outlet valve per cylinder, resulting in such interaction of the levers 33 and culverts 30 and 31 with the inlet 10 and outlet 11 valves in the engine for each cylinder having one inlet and outlet manifold mounted on each side of the cylinder head.