DE102007062606A1 - Combustion engine, particularly diesel engine, particularly for motor vehicle, has working cylinder and piston moving back and forth in working cylinder over predetermined stroke - Google Patents

Abstract

The combustion engine has a working cylinder and a piston moving back and forth in the working cylinder over a predetermined stroke. The working cylinder has a bore diameter predetermined in such a manner that bore diameter gives a predetermined stroke bore ratio for the working cylinder.

Description

The The invention relates to an internal combustion engine, in particular a diesel engine, in particular of a motor vehicle, with at least one working cylinder and one in the cylinder over a predetermined Hub reciprocating reciprocating piston, the working cylinder a predetermined bore diameter D such that for the at least one working cylinder a predetermined Hub bore ratio H / D gives, according to the Preamble of claim 1.

It are charged direct injection diesel engines known commonly as Langhuber with a stroke-bore ratio larger 1 are designed. A few aggregates have an approximately square Hub-bore ratio from 0.98 to 1.02.

at supercharged engines with specific torques> 165 Nm / liter displacement, in particular> 190 Nm / liter of displacement and especially> 250 Nm / liter displacement, the vibration behavior plays a increasingly important role. Especially with 4-cylinder engines lead Mass and gas forces as well as the stiffness of crankshaft and cylinder crankcases to increasingly unfavorable Vibration and acoustic behavior with very long-stroke designed Aggregates (H / D> 1.1), which entail a limitation of maximum torque and power.

From the DE-OS-14 26 082 is a multi-cylinder diesel engine with open combustion chambers is known, wherein the stroke-bore ratio is less than 0.9 and the diameter of the cylinder bore is greater than 10 cm.

Of the Invention is based on the object, internal combustion engines o. G. To improve the type of vibration behavior.

These The object is achieved by an internal combustion engine the o. g. Art solved with the features characterized in claim 1. Advantageous embodiments of the invention are in the other Claims described.

To it is in an internal combustion engine o. g. Art provided according to the invention, that the stroke-bore ratio H / D according to the following Relation is formed, H / D <a - 0.0135 · D for 0 <D ≤ 80 mm and H / D <b for 80 mm ≤ D ≤ 83 mm, where (a; b) = (2.06, 0.98) or (2.03, 0.95) or (2.00, 0.92).

This has the advantage that a highly supercharged, low-emission engine, in particular a diesel engine, is available with vibration optimization. At the same time a reduction in consumption in the New European driving cycle of 0.5 to 0.8 l / 100 km per dm ³ displacement reduction compared to known internal combustion engines is achieved with this low emission supercharged engine.

In a preferred embodiment is the stroke-bore ratio H / D is formed according to the following relation, H / D <a - 0.0135 · D for 60 ≤ D ≤ 80 mm and H / D <b for 80 mm ≤ D ≤ 83 mm, where (a; b) = (2.06; 0.98) or (2.03, 0.95) or (2.00, 0.92).

In Another preferred embodiment is the stroke-bore ratio H / D is formed according to the following relation, H / D <a - 0.0135 · D for 0 <D ≤ 77.77 mm and H / D <b for 77.77 mm ≤ D ≤ 83 mm, where (a; b) = (2.03, 0.98) or (2.00, 0.95) or (1.97, 0.92).

In Another preferred embodiment is the stroke-bore ratio H / D is formed according to the following relation, H / D <a - 0.0135 · D for 60 ≤ D ≤ 77.77 mm and H / D <b for 77.77 mm ≤ D ≤ 83 mm, where (a; b) = (2.03; 0.98) or (2.00, 0.95) or (1.97; 0.92).

In Another preferred embodiment is the stroke-bore ratio H / D is formed according to the following relation, H / D <2.00-0.0135 × D for 0 <D ≤ 75.55 mm and H / D <0.98; 0.95 or 0.92 for 75.55 mm ≤ D ≤ 83 mm, where (a; b) = (2.00; 0.98) or (1.97; 0.95) or (1.94; 0.92) is.

In Another preferred embodiment is the stroke-bore ratio H / D is formed according to the following relation, H / D <2.00-0.0135 × D for 60 ≤ D ≤ 75.55 mm and H / D <0.98; 0,95 or 0.92 for 75.55 mm ≤ D ≤ 83 mm, where (a; b) = (2.00; 0.98) or (1.97; 0.95) or (1.94; 0.92).

A Particularly good vibration optimization is doing for a Internal combustion engine achieved less than six working cylinders having.

Conveniently, the internal combustion engine has a specific maximum torque greater than 170 Nm / liter displacement, in particular greater than 190, 220, 250, 280, 330 or 400 Nm / liter Displacement, on.

Conveniently, the internal combustion engine has a specific maximum power of greater than 50, 55, 60, 65, 70, 75, 80, 85, 90, 95 or 100 kW / liter displacement.

The Internal combustion engine preferably has one, two or more turbochargers on, wherein advantageously the internal combustion engine at least an exhaust gas turbocharger and at least one compressor.

Prefers the turbochargers are parallel or in the form of a register charge or step charging arranged.

A good filling with low swirl flow is achieved by the fact that the internal combustion engine an air flow rate of α _K ≥ 0.10; 0.11; 0.12 or 0.13 and a Tippelmann twist number of ≤ 0.45; 0.40; 0.35 or 0.30.

For the achievement of favorable HC, NO _x and particulate emissions, emission disadvantages due to a low charge movement are compensated for by the fact that the internal combustion engine has a fuel injector with a number of holes of ≥ 8, 9, 10, 12 or 16.

A particularly large piston bowl with improved emission properties is achieved in that the reciprocating piston has a piston recess, which comprises the area of the piston mirror which is> 3 mm inside the Piston edge is located and at the slope of the trough edge of the Value 1 reached. Here, the surface of the piston recess comprises preferably 50, 55, 60, 65, 70 or 75% of the area of the piston mirror.

to better mixture preparation is a maximum injection pressure for the injection of fuel into a combustion chamber of a working cylinder greater than 1,800, 2,000, 2,200, 2,500 or 3,000 bar.

In another exemplary embodiment, the Internal combustion engine four working cylinders, a bore D of 68.0 mm and a stroke H of 73.0 mm, the internal combustion engine prefers a power of 47 kW and a maximum torque of 155 Nm.

In another exemplary embodiment, the Internal combustion engine four working cylinders, a bore D of 81.0 mm and a stroke H of 76.5 mm, the internal combustion engine prefers a power of 110 kW and a maximum torque of 320 Nm.

In another exemplary embodiment, the Internal combustion engine four working cylinders, a bore D of 75.0 mm and a stroke H of 67.0 mm, the internal combustion engine prefers a power of 74 kW and a maximum torque of 250 Nm.

The The invention will be explained in more detail below with reference to the drawing explained. This shows in the only Fig. A graphical Representation of a stroke-bore ratio H / D on the Vertical axis, plotted over the diameter D of the bore in a working cylinder on the right axis.

According to the invention proposed an internal combustion engine, in particular a diesel engine, with working cylinders, each having a bore with a diameter D, and with a in a working cylinder over a predetermined stroke H reciprocating piston short-stroke, d. H. with a stroke-bore ratio H / D <0.98, in particular <0.95, especially <0.92, wherein the diameter D is smaller than 83 mm. This is special preferred that the internal combustion engine any number of cylinders or less than six cylinders.

With particularly small holes, the influence of the mass forces on the vibration behavior tends to decrease because of the smaller piston mass. Therefore, even longer-lasting aggregates can exhibit a satisfactory vibration behavior, in particular those of the formula H / D <2.06-0.0135 × D for D <80 mm and H / D <0.98 for D> 80 mm, in particular H / D <2.03-0.0135 × D for D <77.77 mm and H / D <0.98 for D> 77.77 mm, especially H / D <2.00-0.0135 × D for D <75.55 mm and H / D <0.98 for D> 75.55 mm correspond.

Prefers has an internal combustion engine according to the invention a specific maximum torque of> 170 Nm / liter displacement and in particular> 190/220/250/280/330/400 Nm / liter displacement.

Prefers has an internal combustion engine according to the invention a specific maximum power of> 50/55/60/65/70/75/80/85/90/95/100 kW / liter Displacement on.

Prefers has an internal combustion engine according to the invention more than a turbocharger. The loaders can be parallel be switched, for example, each 3 cylinders act on an ATL, or a Registeraufladung, wherein at small exhaust gas mass flows only 1 ATL charged and at higher exhaust gas mass flows a second ATL is switched in parallel, or a step charge, wherein the exhaust gas is first a high pressure ATL and after flows through a series-connected low-pressure ATL.

Preferably, an internal combustion engine according to the invention - also in the interest of good filling - a low swirl flow, characterized by an air flow rate α _k >0.10;0.11;0.12; 0.13 and a swirl number according to Tippelmann D <0.45;0.40;0.35; 0.30.

For the achievement of favorable HC, NOx and particulate emissions It is inventively provided that the emission disadvantages the low charge movement due to a high number of holes of the injector of greater than or equal to 8; 9; 10; 12 or 16 compensated become. Alternatively or additionally, a particularly large Piston well are provided. The edge of the piston recess comprises the area of the piston mirror which is> 3 mm inside the piston edge and in which the slope of the trough edge assumes the value 1. The Surface of the piston recess preferably comprises> 50; 55; 60; 65; 70; 75% of the area of the piston mirror. For better mixture preparation is supplementary or alternatively a max. Injection pressure of> 1800; 2000; 2200; 2500 or 3000 bar.

With the present invention designed low-vibration and emission-optimized supercharged diesel engine consumption reduction in the New European driving cycle of 0.5 to 0.8 l / 100 km per dm ³ displacement reduction. Diesel engines achievable in the prior art.

In 1 is on a horizontal axis 10 a diameter of a hole D in [mm] and on a vertical axis 12 a stroke-bore ratio H / D (dimensionless) is plotted. lines 14 . 16 and 18 limit the hatched area 20 in this field in which stroke-hole ratios H / D according to the invention are located. This area 20 either extends to the zero values on the horizontal axis 10 and the vertical axis 12 or is through the axes 10 . 12 limited, as shown in the figure.

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 1426082 A [0004]

Claims (23)

Internal combustion engine, in particular a diesel engine, in particular a motor vehicle, having at least one working cylinder and a reciprocating piston which can be moved back and forth in the working cylinder over a predetermined stroke, wherein the working cylinder has a predetermined bore diameter D ( 10 ) such that for the at least one working cylinder a predetermined stroke-bore ratio H / D ( 12 ), characterized in that the stroke-bore ratio H / D ( 12 ) is formed according to the following relation, H / D <a - 0.0135 · D for 0 <D ≤ 80 mm and H / D <b for 80 mm ≤ D ≤ 83 mm, where (a; b) = (2.06; 0.98) or (2.03; 0.95) or (2.00; 0.92). Internal combustion engine according to claim 1, characterized in that the stroke-bore ratio H / D ( 12 ) is formed according to the following relation, H / D <a - 0.0135 · D for 60 ≤ D ≤ 80 mm and H / D <b for 80 mm ≤ D ≤ 83 mm, where (a; b) = (2.06; 0.98) or (2.03; 0.95) or (2.00; 0.92). Internal combustion engine according to at least one of the preceding claims, characterized in that the stroke-bore ratio H / D ( 12 ) is formed according to the following relation, H / D <a - 0.0135 · D for 0 <D ≤ 77.77 mm and H / D <b for 77.77 mm ≤ D ≤ 83 mm, where (a; b) = (2.03; 0.98) or (2.00; 0.95) or (1.97; 0.92). Internal combustion engine according to at least one of the preceding claims, characterized in that the stroke-bore ratio H / D ( 12 ) is formed according to the following relation, H / D <a - 0.0135 · D for 60 ≤ D ≤ 77.77 mm and H / D <b for 77.77 mm ≤ D ≤ 83 mm, where (a; b) = (2.03; 0.98) or (2.00; 0.95) or (1.97; 0.92). Internal combustion engine according to at least one of the preceding claims, characterized in that the stroke-bore ratio H / D ( 12 ) is formed according to the following relation, H / D <a - 0.0135 · D for 0 <D ≤ 75.55 mm and H / D <b for 75.55 mm ≤ D ≤ 83 mm, where (a; b) = (2.00; 0.98) or (1.97; 0.95) or (1.94; 0.92). Internal combustion engine according to at least one of the preceding claims, characterized in that the stroke-bore ratio H / D ( 12 ) is formed according to the following relation, H / D <a - 0.0135 · D for 60 ≤ D ≤ 75.55 mm and H / D <b for 75.55 mm ≤ D ≤ 83 mm, where (a; b) = (2.00; 0.98) or (1.97; 0.95) or (1.94; 0.92). Internal combustion engine according to at least one of the preceding Claims, characterized in that the internal combustion engine has less than six working cylinders. Internal combustion engine according to at least one of the preceding Claims, characterized in that the internal combustion engine a specific maximum torque of greater 170 Nm / liter displacement, especially larger 190, 220, 250, 280, 330 or 400 Nm / liter displacement. Internal combustion engine according to at least one of the preceding claims, characterized the internal combustion engine has a specific maximum power of greater than 50, 55, 60, 65, 70, 75, 80, 85, 90, 95 or 100 kW / liter displacement. Internal combustion engine according to at least one of the preceding Claims, characterized in that the internal combustion engine having one, two or more turbochargers. Internal combustion engine according to claim 10, characterized that the internal combustion engine at least one exhaust gas turbocharger and has at least one compressor. Internal combustion engine according to claim 10 or 11, characterized characterized in that the turbocharger is parallel or in the form of a Register charging or step charging are arranged. Internal combustion engine according to at least one of the preceding claims, characterized in that the internal combustion engine has an air flow rate of α _k ≥ 0.10; 0.11; 0.12 or 0.13 and a Tippelmann twist number of ≤ 0.45; 0.40; 0.35 or 0.30. Internal combustion engine according to at least one of the preceding Claims, characterized in that the internal combustion engine a fuel injector with a number of holes of ≥ 8, 9, 10, 12 or 16 has. Internal combustion engine according to at least one of the preceding Claims, characterized in that the lifting piston a Piston well, which is the surface of the piston mirror includes> 3 mm lies within the piston edge and at the slope of the trough edge reaches the value 1. Internal combustion engine according to claim 15, characterized that the area of the piston recess 50, 55, 60, 65, 70, 75% the surface of the piston mirror comprises. Internal combustion engine according to at least one of the preceding Claims, characterized in that a maximum injection pressure for injecting fuel into a combustion chamber of a Working cylinder is greater than 1,800, 2,000, 2,200, 2,500 or 3,000 bar. Internal combustion engine according to at least one of the preceding Claims, characterized in that the internal combustion engine four working cylinders, a bore D of 68.0 mm and a stroke of 73.0 mm. Internal combustion engine according to claim 18, characterized that the internal combustion engine has a power of 47 kW and a maximum Torque of 155 Nm. Internal combustion engine according to at least one of the claims 1 to 17, characterized in that the internal combustion engine four Working cylinder, a bore D of 81.0 mm and a stroke of 76.5 mm. Internal combustion engine according to claim 20, characterized that the internal combustion engine has a power of 110 kW and a maximum Torque of 320 Nm. Internal combustion engine according to at least one of the claims 1 to 17, characterized in that the internal combustion engine four Working cylinder, a bore D of 75.0 mm and a stroke of 67.0 mm. Internal combustion engine according to claim 22, characterized that the internal combustion engine has a power of 74 kW and a maximum Torque of 250 Nm.