SU800402A1 - Exhaust manifold of supercharged i.c.engine - Google Patents

Description

The invention relates to mechanical engineering ^ namely, to engine building, and in particular to a device for exhaust systems of supercharged internal combustion engines.

There are known exhaust manifolds of supercharged internal combustion engines containing ⁵ exhaust pipelines, each of which combines exhaust elements in pairs with offset exhaust phases and is connected to a common pulse converter equipped with exhaust diffuser, transition cylindrical and inlet confuser sections and a flow separator installed in confuser site [1].

In known exhaust manifolds, the confluent section is formed by outlet sections of two exhaust pipelines connected at an angle to one another; therefore, one pulse converter does not allow combining more than four cylinders.

The main disadvantage of the known devices is that they cannot be used in multi-cylinder engines. So, for example, when the number of cylinders is a multiple of two, we have to install additional pulse converters, which, when connected in series, clutters the exhaust system and leads to additional losses of the available energy of the exhaust gases. Parallel connection of additional pulse converters to a multi-start turbine leads to an increase in ventilation losses in the turbocharger of the engine boost, which also reduces the useful use of available exhaust gas energy.

Due to the fact that in the cylindrical section of the converter, only two flows (active and passive) are combined at the inlet of the diffuser, the nonuniformity of the gas flow velocity profile is preserved, which reduces the efficiency of converting the kinetic energy of the gas into pressure, and also weakens the ejection of the passive flow by active the entrance to the mixer and thereby degrades the purge of the combustion chamber, reducing the indicators of the combustion process and impairing fuel efficiency of the engine.

In addition, the exhaust manifold of an engine with such a pulse converter is ineffective or completely unsuitable for multi-cylinder diesel engines with a number of cylinders not a multiple of four, especially for a turbocharger with a single-start turbine, which has a higher efficiency in comparison with the partial supply of gases.

The purpose of the invention is the reduction of losses, available energy of the exhaust gases of an internal combustion engine.

This goal is achieved by the fact that the flow separator is made in the form of two groups of plates of different lengths, alternating between each other, mounted radially and forming sector cameras, each of which is connected to the exhaust pipe, and the plate length of one group is 0.65-0.75 the lengths of the plates of the second group, and one of the exhaust pipelines is located in the pulse converter along the axis of the confuser. Moreover, the outlet cross-sectional area of the confuser section is made in accordance with the relation f = (0.81-0.83) (1 +) F _{mo) x} , where F _max is the effective cross-section with full opening of the exhaust organs of one cylinder;

Ψ is the ratio of the total time section of the simultaneously open exhaust organs to the time section of the exhaust organs of one cylinder;

f - the outlet section area concentration ³⁵ fu Zorn portion.

In FIG. 1 shows the described exhaust manifold of an engine with an even number of combined pipelines, a general view, 'in FIG. 2 - section A — A of the input section of the 48 pulse converter to fit. 1; in FIG. 3 - input section with an odd number of combined pipelines, general view; in FIG. 4 - same, section B — B in FIG. 3; in FIG. 5 is the same, section B-B at 45 of FIG. 4; in FIG. 6 - graphically shows the overlapping time-section of the exhaust organs of an 8-cylinder engine; in FIG. 7 - graphically shows the time section of the exhaust bodies of a 14-cylinder engine. fifty

The described exhaust manifold, for example for an 8-cylinder engine, <includes exhaust bodies (not shown) of the cylinders 1, connected through the exhaust pipes 2 to the exhaust pipes 3 and to a common converter 4 output pulses, equipped with an exhaust diffuser 5, transitional cylindrical 6 and input confuser 7 sections. The confuser section 7 with the flow separator 8 installed therein is a mixer 9 of gas flows. The separator 8 flows is made in the form of two groups of plates 10 and 11 of different lengths, which form the sector chambers 12. The exhaust pipes 3 combine pairwise exhaust bodies with offset phases of the release. The pulse converter 4, with its output diffuser section 5, is connected to equalization tank 13 and to the boost unit 14. One of the pipelines is located in the pulse converter along the confuser axis and is equipped with a nozzle 15. The output section 16 of the confuser section 7 has a well-defined value of its area.

The output sections of the pipelines 3 are connected directly to the sector chambers 12, which are formed by plates 10 and 11 mounted radially and alternating between each other in the confuser inlet section 7 of the mixer 9. The length of the plates of the first group 10 is chosen to ensure the optimal flow rate in the output section of the sector chambers 12 the range of 0.65-0.75 of the length of the plates of the second group 11.

The through section ^ of the exhaust pipes and pipelines 3 is selected depending on the degree of engine boost by the boost pressure and the crankshaft speed in the following limits ^ max <f _n 6 F,!

where F _n F _max - respectively, the geometric and effective cross-section with full opening of the exhaust organs of one cylinder.

The output section 16 of the confuser section 7 is made in accordance with the relation f = (0.81-0.83) (1 + Ψ _Σ ) F _max , where f is the area of the output section of the confuser

zorny plot; the ratio of the total time section of simultaneously open exhaust organs to the time section of the exhaust organs of one cylinder.

The value is the relative value of the time-section of the overlapping phases of the release of the cylinders, united by sector cameras 12 for the full period from the opening of the exhaust organs of one cylinder. For an 8-cylinder engine, the overlapping time-sections of the exhaust bodies for the period are shown in FIG. 6, where the passage section F is plotted along the ordinate axis, and

I along the abscissa - the period of the opening of the exhaust organs ΐ. Value for considering;

This example is determined by planimetricizing the areas under the curves, a ^, c ^ d, e, i.e.

where, Vd and is the time-section of the exhaust organs of various cylinders.

The coefficient '0.81-0.83 in the above ratio is the experimental value of the optimal narrowing of the passage section of each sector chamber 12 to ensure optimal passive flow ejection active on the cut of the plates of the first group 10 and is valid for all types of diesel engines.

The values of Pmax and are selected taking into account the design parameters of a specific ‘• gas distribution system of the diesel in question. Therefore, the ratio for determining the output section f of the sector cameras 12 is generalizing and acceptable for all types of diesel engines.

The angle of convergence a and the length ί of the confuser inlet section 7 of the mixer 9 are taken from the condition of ensuring a minimum pressure loss and are within:

a = 40-60 °; C 0.565 ΥΓ

The work of the exhaust manifold of a supercharged internal combustion engine is as follows.

The exhaust gases in the order of the cylinders are supplied through exhaust pipes _: 2 to the pipelines 3, through which they approach the sector chambers 12. The shape of the rotation bodies attached to the sector chambers 12 (Fig. 2) in the pipes 3 aligned with the outlet cross sections reduces the input resistance and reduces loss of pressure during the passage of exhaust gases through them.

The present invention converts the pulses of the exhaust of a multi-cylinder engine provides the supply of exhaust gases to a single-flow turbine, which has a higher efficiency (compared to multi-flow) as a result of reducing ventilation losses. In addition: it is suitable for an even number of pipelines 3, combining the exhaust pipes of two cylinders (Fig. 1 and 2), and odd.

In FIG. 3 shows a general view of the inlet section 7 of the mixer 9 of the multi-chamber pulse converter 4, made for an odd number of pipelines 3. The main difference in this case is that one of the pipelines 3 is located in the center of the inlet section 7 and is equipped with a nozzle 15. · The remaining pipelines 3 connected with sector cameras 12. The angle of convergence of cp800402 4 la 15 of the central pipeline 3 is equal to the angle of convergence a of the confuser inlet section 7 of mixer 9. The exit section 'and the length of the nozzle 15 are equal to f _c = (0 , 81-0.83) Fmax, ¹⁰

The design ratios f, f, B and a of the exhaust manifold of the combined ICE with an odd number of pipelines 3 are determined by the above 15 ratios. Overlap time-sections of exhaust valves for a 14-cylinder engine. graphically represented in FIG. 7.

The positive effect of the implementation of the proposed exhaust manifold can be reflected in a decrease in the available energy loss, since the design of the proposed multi-chamber pulse converter provides the supply of exhaust gases to a one-way turbine with less ventilation losses.

As a result of combining the proposed multi-chamber design with more than four cylinders, one of the pulse converters, 30 the most complete alignment of the gas flow velocity profile at the inlet of the diffuser occurs, which improves the efficiency of converting the kinetic energy of the exhaust gases into pressure and, therefore, ₃₃ reduces the loss of available gas energy during transportation to a turbocharger boost.

Expansion contact surface interaction of active and passive heavy streams entering the mixer intensifies the effect of ejection, reducing the back pressure to the piston at the time of the combined venting sectorial chambers of cylinders, which reduces the negative work of pumping strokes' and hence, improves fuel ekono ⁴⁵ michnost engine.

As a result of increased ejection eff. The quality of gas exchange and jg indicator indicators of the internal combustion engine are improved.

The most complete use of the available energy of exhaust gases, for example for _ss diesel engines of type 8CHN9, 5/10, can provide a decrease in average operating fuel consumption by 3 g / e l ^ s - h, which, when diesel engines are produced in 2000 units, will give an economic effect in total 350,000 rubles.

Ί

Claims (3)

(54) EXHAUST COLLECTOR OF INTERNAL COMBUSTION ENGINE WITH SUPERCHARGED COMBUSTION AND WRONG EFFICIENCY EFFICIENCY OF THE ENGINE. In addition, the outboard engine manifold with such a pulse converter is ineffective or completely unsuitable for multi-cylinder diesel engines with a number of cylinders not multiple of four, especially for a turbo-compressor with a single-flow turbine, which has a higher efficiency than other gas supply. The purpose of the invention is to reduce the loss of the exhaust energy of an internal combustion engine. This goal is achieved by the fact that the flow divider is made in the form of two groups of plates of different lengths alternating with each other, installed radially and forming sector chambers, each of which is connected to an exhaust pipe, the length of the plates of one group being 0.65-0, 75 of the length of the plates of the second group, and one of the exhaust pipelines is located in the impulse converter along the confuser axis. The area of the exit section of the confuser section is made in accordance with the ratio f (0.81-0.83) (1 + V) where Rtah is the effective flow area with full opening of the exhaust bodies of one cylinder; H is the ratio of the total time — of a section of simultaneously open exhaust organs to time — of a section of the exhaust bodies of one cylinder; f is the area of the exit section of the confused section. FIG. Figure 1 shows the described exhaust manifold of an engine with an even number of pipelines to be combined; a general view; in FIG. 2 - section AA of the input section of the pulse converter in FIG. G, FIG. 3 — inlet section with odd number of united pipelines, general view; in fig. 4 is the same, section BB in FIG. 3; in fig. 5 is the same, section BB in FIG. four; in fig. 6 - graphically shows the overlap of time - the cross section of the exhaust bodies of an 8-cylinder engine; in fig. 7 - graphically shows the time-section of the exhaust bodies of a 14-cylinder engine. The described exhaust manifold, for example, for an 8-cylinder engine, includes exhaust bodies (not shown) of cylinders 1, connected through exhaust pipes 2 to exhaust pipes 3 and to a common converter 4 of exhaust pulses, equipped with exhaust 6, transition cylindrical 6 and input confused 7 sites. The distributor section 7 with the separator 8 streams installed in it is a mixer 9 of gas streams. The section 8 of the flow is made in the form of two groups of plates 10 and 11 of different lengths which form sector chambers 12. The outgoing pipelines 3 combine in pairs the exhaust bodies with the effective phases of the release. The converter 4 pulses with its output diffuser section 5 is connected to the surge tank 13 and to the charge unit 14. One of the pipelines is located in the converter of pulses along the confuser axis and provided with a nozzle 15. The output section 16 of the confuser section 7 has a well-defined value of its area. The output sections f of the pipelines 3 are directly connected to the sector chambers 12, which are formed by plates 10 and 11, which are installed radially and alternating with each other in the confused entry section 7 of the mixer 9. The length of the plates of the first group 10 to provide the optimum flow rate in the output section of the sector chambers 12 is selected in the range of 0.65-0.75 from the length of the plates of the second group 11. The passage section f, the exhaust nozzles 2 and pipelines 3 are chosen depending on the degree of engine forcing by the boost pressure and the frequency is rotated crankshaft within the following limits Pmax f "6 F, 1 rjDie Fp FfTiax respectively geometric and effective flow cross-section with the full opening of the outlet cylinder bodies. The output section 16 of the confused section 7 is made in accordance with the ratio f (0.81-0.83) (1 + 4-5.) Fmax, where -f is the area of the output section of the confused section; the ratio of the total time — the cross sections of simultaneously open exhaust bodies to the time – cross section of the exhaust bodies of one cylinder. Vj value. is a relative ve; shchinu time -slice of overlapping phases of cyander release, combined by sector chambers 12 for the entire period of opening t; j of exhaust bodies of one cylinder. For an 8 cylinder engine, the overlap time is the ε-section of the exhaust organs for the period t. shown in FIG. 6, where the flow section F is plotted along the ordinate axis, and the period of opening of the exhaust organs t is shown along the abscissa axis. The magnitude of Y. for the example under consideration is determined by the planimetric measurement of the placers under the curves, a ,, e, i.e. Y o-, where a, b Ci - time - the cross section of the exhaust bodies of the various cylinders. The ratio of 0.81-0.83 in the above ratio is the experimental value of the optimal narrowing of the flow area of each sector chamber 12 to ensure optimum ejection of the passive flow active on the cut of the plates of the first group of 10 n is valid for all types of diesel engines. The values of Fmax and are selected taking into account the design parameters of a particular -CHcfe of the gas distribution of the diesel under consideration. Consequently, the ratio for determining the output section f of the sector chambers 12 is of a general nature to acceptable for all types of diesel engines. The angle of convergence a and the length of &amp; confuser inlet section 7 of the mixer 9 is taken from the condition of ensuring minimum head loss and is within; a 40-60 °; E 0,565 YfT The operation of the exhaust manifold of an internal combustion engine with supercharging is as follows: Exhaust gases in order, the cylinder works through the outlet nozzles; 2 to the pipeline: m 3, which fit the sector chambers 12. Given the sector chambers 12 body shape rotation (Fig. 2) of the pipelines 3 which are coaxial with the outlet sections, reduces the input resistance and ensures a reduction in the pressure loss when the exhaust gases pass through them. The proposed invention for converting a multi-cylinder engine's output pulses provides a supply of exhaust gases to a single-passage turbine, which has a high efficiency (as compared to a multi-output) as a result of a reduction in ventilation losses. Besides, ; It is suitable for even the number of pipelines 3, combining outlets of two cylinders (Fig. 1 and 2), and odd. FIG. Fig. 3 shows a &amp; a view of the inlet section 7 of the mixer 9 of the multi-chamber pulse converter 4, made for an odd number of pipelines 3. The main difference in this case is that one of the pipelines 3 is located in the center of the inlet section 7 and provided with a nozzle 15. The rest of the pipelines 3 are connected to the secondary chambers 12. The convergence angle of the central pipeline 3 is made equal to the convergence angle Q of the confused part 7 of the mixer 9. The output section fd and the length of the nozzle 15 are equal to fc (0.81-0 , 83) Fmax, (Constructive ratios f., F, E and a of the considered exhaust manifold of a combined ICE with an odd number of pipes 3 are determined by the previously installed 1 M ratios. The overlap time is the section of the exhaust valves for a 14-cylinder engine, graphically presented on the fcg 7. The positive effect of the implementation of the proposed exhaust manifold may be reflected in the reduction of the available energy in the loss, since the design of the proposed multi-chamber pulse converter provides exhaust gas to a single inlet turbine with less ventilation losses. B. As a result of combining a pulse converter of the proposed multi-chamber design with more than four cylinders, the profile of the gas flow velocity at the entrance to the diffuser is most fully equalized, which contributes to the efficiency of conversion of the kinetic energy of exhaust gases into pressure and, therefore, reduces the loss of available gas energy during transportation it to the turbocharger nalduva. The expansion of the surface of contact between the interaction of active and passive flows at the inlet to the mixer enhances the ejection effect, which reduces the pressure of the piston at the time of release of gases from the cylinders of the sector chambers, which reduces the negative operation of the pump strokes and, consequently, increases the fuel economy of the engine. As a result of the enhancement of the injection effect, the quality of gas exchange and indicator indicators of the internal combustion engine are improved. The most complete use of the available energy of exhaust gases, for example, for diesel engines of type 8ЧН9, 5/10, can provide a reduction in average operating fuel consumption by 3 g / hp-h, which, with the production of diesel engines of 2000 pieces, will give an economic effect in the amount of 350000 rubles. 78 Claim 1. Intake manifold I of an internal combustion engine with supercharging, containing exhaust pipes, each of which combines in pairs the exhaust bodies with alternating exhaust phases and is connected to a common impulse converter, equipped with an exhaust diffuser, transitional cylindrical and inlet confuser section and a flow separator installed in an extrusion section, characterized in that, in order to reduce the loss of available energy, the flow separator is made in the form of two groups of in different lengths, interlaced between themselves, installed radically and forming sector chambers, each of which are connected to an outlet piping, the plates of one group being 0.65-0.75 of the length of the plates from the second group. 2. The collector according to claim 1, wherein the terminal section of the outlet section is made in accordance with the ratio f (0.81-0.83) (1 + Od) Fmax. e Fmax - effective flow area with full opening of the exhaust bodies of one cylinder; Vj is the ratio of the total time of a section of simultaneously disconnected exhaust bodies to time of a section of the exhaust bodies of one cylinder; f is the area of the output section: the fusor area. 3. The collector on PP. 1 and 2, that is, with the fact that one of the exhaust pipes is located in the imls converter on the confuser axis. Sources of information taken into account in the examination 1. Pateit France N 2147426, cl. FO N7 / 00, photo 1973. Iput. f —N 7 riff f ///// AA P 14 / (Pltt.3 Jf (fut. F