DE102004038737A1 - Impulse charger with axial valve - Google Patents

Abstract

The invention relates to a pulse charger for a combustion engine (1). The impulse charger (13) is assigned to the inlet side (2) of the internal combustion engine (1) and received in an air feed (9). The impulse charger (13) at least partially releases or closes the flow cross-section (26) for the combustion air (27). The impulse charger (13) is designed as an axial valve (30).

Description

technical area

to Improvement of the cylinder filling with combustion air come on internal combustion engines charging devices for use. The superchargers can be used as exhaust gas turbochargers or mechanically driven loader or be designed as a pressure wave loader and increase in the intake tract of an internal combustion engine the pressure level, at open Inlet valves of the internal combustion engine a higher degree of filling to reach the cylinder. At lower speeds of internal combustion engines occurs in exhaust gas turbochargers on the so-called "turbo lag", since due to the lower exhaust gas flow rate the discharged from the turbine to the compressor impeller of the exhaust gas turbocharger mechanical power for increasing the pressure in the intake tract of the internal combustion engine no longer sufficient.

at Exhaust gas turbochargers which are used on internal combustion engines, be it self-igniting or spark-ignited internal combustion engines, used, occurs in the lower speed range of the internal combustion engine the above already mentioned Turbo lag on. In this operating state of an internal combustion engine extends the exhaust gas flow, that of the internal combustion engine is produced, not to the compressor impeller of the exhaust gas turbocharger to drive at a speed which leads to a sufficient pressure increase in the Intake tract of the internal combustion engine could lead.

A Possible solution, the above-described Betriebscharakteristikum exhaust gas turbochargers To be master, lies in the exhaust gas turbocharger, e.g. electrical to provide drivable additional units, for example, via a One-way clutch from reaching a certain lower speed value the internal combustion engine are switchable and after crossing a certain, the turbo lag avoiding speed of the internal combustion engine can be thrown off again, what about, for example an overrunning clutch or an overrunning clutch or the like can take place.

Out Prior art pulse boosters are known. Become a pulse loader in the intake of an internal combustion engine on the inlet side arranged the internal combustion engine. The previously used Impulse loaders work according to the flap principle and have one in the charge air supply integrated to the internal combustion engine flap mimic. The used flap principle, however, has the considerable disadvantage on that the stability of the flaps owing to the extremely short Switching times and the frequent mechanical contact with stop surfaces still unsatisfactory fails. The frequent Stopping the driven flaps such impulse loader on the Wall of the charge air supply on the one hand goes hand in hand with mechanical wear and on the other hand leads to a not inconsiderable noise development in the intake tract. The with increasing operating time of the internal combustion engine on the flaps of the impulse charger used wear on the other hand leads to the fact that the flaps in the closed state no longer completely tight are and are increasing with time the leakage air flow of the charge air adjusts along the no longer tightly closing flaps, which the efficiency of such a trained impulse charger in the intake an internal combustion engine negatively affected.

at a design of the intake in an internal combustion engine used impulse loader as a roller rotary valve (for example in shape a transverse drilled cylinder), the volume of the impulse charger relatively large, around the entire opening cross-section to cover the charge air supply. In addition to the big one Space volume such ausgestalteter impulse charger have this the disadvantage of big moving masses, so their use has significant requirements to the drive and on the other hand to large moments of inertia leads. Short switching times can be designed as a roller rotary valve Pulse loaders difficult to reach.

presentation the invention

According to the invention, it is proposed to equip a pulse loader with an axial valve, which as a modified axial ball bearing is formed. The axial ball bearing is modified so that in the two races of the Axial ball bearings in the sections, seen in the circumferential direction, between the rolling bodies, be it balls, be it cylinders, axial bores are introduced. One of the bearing rings of the axial ball bearing is fixed to the housing unmounted while the remaining second bearing ring of the modified thrust ball bearing a rotating drive oscillates rotationally or rotationally actuated can be. By the rotation of the movable of the bearing rings relative to the housing assembled bearing ring, a pulse loader is shown, depending on Whether the two bearing rings passing through axial bores with each other aligned or whether the holes are closed.

The inventively proposed Lö This solution is characterized by the fact that it has a high insensitivity to deposits compared with pulse chargers according to the flap principle, since this is self-cleaning. The self-cleaning is brought about by the fact that the bearing cage provided in the thrust bearing serves as a stripping surface. As a further advantage inherent in the invention proposed solution is emphasized that in a rotationally oscillating actuation of the movable bearing ring relative to the fixed bearing ring mounted housing depending on the number of bearing bodies, be it balls, be it roles, only a small angle of rotation is needed, such as 22, 5 °. The inventively proposed, used as an axial valve modified thrust bearing is further characterized by a compact design. This brings with oscillatory rotary actuation considerable dynamics advantages in terms of low inertia with it, so that a high oscillation frequency can be realized. In the case of a monotone rotational drive taking place in a rotational direction, due to the compact design of the axial valve proposed according to the invention, only slight moment of inertia effects result from a required change in the angular velocity.

Finally, be emphasized that the inventively used as impulse charger modified thrust bearing has no mechanical stops, so that a mechanical wear is almost impossible, once apart from the service life of the thrust bearing after usual Bearing calculation methods.

When Drive, be it as oscillating rotary drive, be it as monotonously acting in a direction of rotation rotating drive can an electric motor can be used, the design condition within the bearing ring can be attached, which is the volume of construction of the present invention as a pulse loader used thrust bearing low influenced, in particular compared with impulse loaders on the flap principle as well as known from the prior art impulse loader as a roller rotary valve are formed. Due to the complete absence of mechanical Attacks, those proposed by the invention solution allowed, the proposed axial valve is characterized by a extremely low noise level because there is no impact with high frequency moving parts of mechanical stops.

drawing

Based In the drawings, the invention will be described below in more detail.

It shows:

1 the inlet side of an internal combustion engine with individual components of the intake tract,

2 a top view of the axial valve,

3 a cross section through the bearing rings and the bearing cage of the axial valve,

4.1 . 4.2 , and 4.3 individual components of the axial valve in partial plan view, Schnittdar position and complete plan view and

5.1 to 5.3 Variants of a drive for one of the bearing rings.

variants

The representation according to 1 Internal combustion engine with components of the intake tract and the exhaust tract can be seen.

In the illustration according to 1 is as an internal combustion engine 1 a spark-ignited internal combustion engine together with their components in the intake system or in the exhaust system shown. The internal combustion engine 1 is the combustion air required for combustion in the combustion chamber via an air inlet 4 supplied, which may be associated with an air mass meter and an air filter element. The combustion air flows to an air supply 9 and can be a compressor part 6 an optionally the internal combustion engine associated charging device 5 happen. The charging device 5 includes the already mentioned compressor part 6 and a turbine part 7 , The compressor part 6 and the turbine part 7 are about a wave 8th connected with each other. The optionally precompressed combustion air flows to the air supply 9 to, an intercooler happens 10 , which is a charge air sensor 11 can be downstream. The in the air supply 9 flowing combustion air is denoted by the reference numeral 27 symbolized arrow symbolizes. After passage of the charge air sensor 11 the combustion air flows 27 via a throttle device 12 a pulse loader 13 to. The impulse charger 13 is just in front of the inlet side 2 the internal combustion engine 1 arranged.

The internal combustion engine, which may be a 4-, 5-, 6-, 8-, 10-, or 12-cylinder internal combustion engine, includes a number of intake valves corresponding to the number of cylinders 15 , In the 1 exemplified internal combustion engine 1 also includes ignition devices 16 , which are assigned to the individual cylinders.

On the exhaust side 3 the internal combustion engine 1 are in a number of cylinders corresponding number of exhaust valves 17 added. About the exhaust valves 17 the exhaust gas flows into an exhaust gas duct 23 to and acts on the arranged in this turbine part 7 the charging device 5 , Optionally available in the exhaust duct 23 a waste gate 24 be installed over which of an exhaust pipe 25 inflowing exhaust gas flow can be varied.

Immediately behind the impulse charger 13 there is a fuel injector 14 over which into a combustion chamber 18 with the inlet valve open 15 Fuel can be injected. Inside the combustion chamber 18 becomes with closed inlet valve 15 and closed exhaust valve 17 that during the upward movement of the piston 19 compressed mixture ignited and exploded.

For completeness, it should be mentioned that the internal combustion engine 1 at least one knock sensor 20 , a temperature sensor 21 for detecting the coolant temperature and in the region of the crankshaft flywheel, a speed sensor 22 assigned.

The representation according to 2 is to be taken from an axial valve proposed according to the invention.

About the inlet side 2 the internal combustion engine 1 assigned impulse charger 13 is when the inlet valve is open 15 the degree of filling of the combustion chamber 18 influenced by the air mass required for combustion. According to the invention it is proposed that the impulse charger 13 as axial valve 30 , as in 2 shown in plan view, is formed. As axial valve 30 becomes one through axial bores 33 Modified axial ball bearing used. The thrust bearing comprises a first bearing ring 34 and one in 2 not shown, in plan view behind the first bearing ring 34 lying second bearing ring 35 , One of the two bearing rings 34 . 35 can be moved in a monotonically rotating or rotationally oscillating by a trained example as an electric drive drive in one direction. One of the two bearing rings 34 respectively 35 can be attached to the inner wall of the air supply 9 rotatably secured while the mentioned drive on the other of the two bearing rings 34 . 35 acts and this drives either monotonously rotating in one direction or, as already mentioned, rotationally oscillating. In a rotationally driven oscillating bearing ring is depending on the number of rolling elements used in the modified thrust bearing 31 only a small rotation angle is needed, for example 22.5 ° in 2 illustrated embodiment of the invention proposed impulse charger.

The representation according to 2 is removable, that in this embodiment, the rolling elements 31 are formed as spheres that are of an in 2 only hinted, but 3 closer removable bearing cage between the bearing rings 34 respectively 35 are fixed.

In the illustration according to 2 stand the individual axial bores 33 that the first bearing ring 34 and the second bearing ring 35 each pass through, aligned over each other and allow passage through the air supply 9 (see illustration according to 1 ) passing combustion air flow 27 ,

From the sectional view of the modified thrust bearing according to 3 shows that in this embodiment spherical trained rolling elements 31 from a storage cage 36 made of plastic material or of metallic material, between the first bearing ring 34 and the second bearing ring 35 are fixed. Instead of in 3 shown, spherical trained rolling elements 31 These may also be designed as cylindrical rollers or as tapered rollers or the like. 3 is removable, that both the first bearing ring 34 , as well as the second bearing ring 35 of axial bores 33 evenly over the circumference of the first bearing ring 34 and the second bearing ring 35 are interspersed, interspersed.

The spherically shaped rolling elements 31 lie as shown in 3 at contact surfaces 37 of the first bearing ring 34 as well as on contact surfaces 38 of the second bearing ring 35 at. One of the two bearing rings 34 respectively 35 the inventively proposed axial valve 30 is on the inner wall, which is the flow cross section 26 the air supply 9 limited, rotationally fixed, while the remaining of the bearing rings 34 . 35 is movable relative to the housing fixedly arranged bearing ring. This is done by an electric motor drive.

According to the in the 2 and 3 shown first embodiment of the impulse charger proposed according to the invention 13 this is achieved by an axial valve designed as a modified axial ball bearing 30 shown. In the two bearing rings 34 . 35 as well as in the camp cage 36 are distributed evenly over the circumference axial bores 33 attached, characterized by mutual rotation of the bearing rings 34 . 35 in overlap or from their aligned overlap. The execution of the bearing cage 36 is such that when the axial flow through the axial valve 30 and in corresponding rotational position of the first bearing ring 34 of the second bearing ring 35 as well as the bearing cage 36 to each other sets a pneumatic sealing. Thus, depending on the relative Ver angle of rotation of the rotatable bearing rings 34 . 35 for bearing ring fixed to the housing causes a sealing or release of flow cross-sections, wherein the flow-through cross-section of the geometry and the number of axial bores formed in the axial valve 33 depends.

An axial tension of the axial valve 30 ie a tension of the first bearing ring 34 against the second bearing ring 35 requires a rolling movement of the rolling elements 31 , whereby an alternating opening or closing of the axial valve 30 can achieve.

The representation according to 4.1 is a bearing ring segment 39 one of the two bearing rings 34 . 35 refer to. In the in 4.1 shown bearing ring segment 39 are two spaced apart axial bores 33 admitted. It should be noted that the axial bores 33 as shown in 4.1 in a bearing ring segment 39 , For example, the first bearing ring 34 in a corresponding manner also in the corresponding bearing ring segment of the second bearing ring 35 are formed.

4.2 shows in greatly enlarged scale a partial section through the invention proposed axial valve 30 , Between the first bearing ring 34 and the second bearing ring 35 are spherical trained rolling elements 31 admitted. These are over the bearing cage 36 held together, in turn, a ring 42 having, in the illustration according to 2 spherical trained rolling elements 31 encloses on the outside. The camp cage 36 also has sprags 43 on, which at the facing each other inside of the first bearing ring 34 and the second bearing ring 35 issue. In the area of rolling elements 31 are in the bearing rings 34 . 35 of the axial valve 30 drilling 40 respectively 41 educated.

The representation according to 4.3 is a plan view of the axial valve 30 to remove trained impulse loader. Between the first bearing ring 34 and the second bearing ring 35 there is a storage cage 36 who has the bearing ring 42 contains. The bearing ring 42 is in terms of its outer diameter complementary to the outer diameter of the first bearing ring 34 and second bearing ring 35 educated. By the camp cage 36 trained clamp body 43 and the rolling elements 31 become the two bearing rings 34 . 35 at axial preload of the axial valve 30 kept at a defined distance from each other. One of the two bearing rings 34 . 35 - as already mentioned above in connection with the 2 and 3 mentioned - rotatably on the inside of the air supply 9 stored while the other of the two bearing rings 34 . 35 relative to the rotationally fixed arranged the bearing rings 34 . 35 remains rotatable.

The impulse charger described in more detail above 13 With respect to the known from the prior art designs of impulse loaders according to the flap principle on a very compact design, which results in considerable advantages in terms of moving masses with oscillating rotary actuation. Even with a drive in a monotone direction only slight inertial effects result from a required change in the angular velocity. In particular, it should be emphasized that with an oscillatory rotary actuation of the movable of the two bearing rings 34 . 35 depending on the number of balls only a small angle of rotation is required, which in the embodiment according to the 2 and 3 only 22.5 °.

Due to the design of the bearing cage 36 with sprags 43 (see illustration according to 4.3 ) can at the inventively proposed thrust bearing 30 a high sealing effect can be achieved. In the clamp body 43 of the bearing cage 36 that of a ring 42 surrounded, are also axial bores 33 introduced, whose diameter that of the axial bores 33 in the two bearing rings 34 respectively 35 equivalent. Are the axial holes 33 the bearing rings 34 . 35 as well as in the sprags 43 of the bearing cage 36 introduced axial bores 33 staggered to each other, so has the axial valve 30 a high sealing effect, which favors a use as impulse charger very. Are the axial holes 33 the two bearing rings 34 and 35 however, with the in the clamp body 43 of the bearing cage 36 introduced axial bores 33 in overlap, the entire flow cross-section is available.

The in the 5.1 to 5.3 illustrated embodiments of an electric drive for the rotatable of the two bearing rings 34 . 35 represents the first bearing ring 34 the rotationally or rotationally oscillatable movable of the two bearing rings 34 respectively 35 represents.

In the illustration according to 5.1 For example, there is an electric drive designed as an electric motor 44 within the passage opening 32 of the axial valve 30 , The electric drive 44 acts on a contact surface 46 , in this embodiment, on the inside of the first bearing ring 34 is applied. This allows the relative to the second bearing ring 35 rotatable first bearing ring 34 both rotationally monotonically driven in a circumferential direction and rotationally oscillating, while the second bearing ring 35 is arranged rotationally fixed. This in 5.1 illustrated axial valve 30 includes the first bearing ring 34 , the second bearing ring 35 as well as within the bearing cage 36 arranged rolling elements 31 , which are formed here as spheres. In the area of rolling elements 31 are both the first bearing ring 34 as well as the second bearing ring 35 with holes 40 respectively 41 Mistake.

In the in 5.2 illustrated embodiment of a rotary drive for one of the two bearing rings of the axial valve is the electric drive 44 with a drive element 45 provided, which can be designed both as a pinion or as a friction wheel. In this case, the pinion or friction wheel acts 45 on a contact surface 46 at the front of the first, driven bearing ring 34 , When using a pinion 45 can the contact surface 46 be formed as a gearing; when configuring the drive element 45 as a friction wheel is the contact surface 46 provided with a good frictional engagement and thus a good torque transmission enabling coating.

The representation according to 5.3 is a further embodiment of a drive of the movable of the two bearing rings 34 . 35 refer to. In this embodiment, the electric drive comprises 44 also a drive element 45 which can be designed both as a pinion and as a friction wheel. In this embodiment, the contact surface 46 laterally on the driven, first bearing ring 34 educated.

In the 5.2 respectively 5.3 illustrated electric drive 44 The property resides in the fact that this outside of the passage area for through the axial valve 30 is arranged to be conveyed medium, ie the through hole 33 the two bearing rings 34 . 35 are not in terms of their cross section by the electric drive 44 impaired. The in the 5.2 respectively 5.3 illustrated axial valves 30 also comprise spherically shaped rolling elements 31 inside the storage cage 36 which in turn are of a ring 42 is enclosed. Also in these embodiments, the bearing rings 34 . 35 in the region of the spherical rolling elements 31 with holes 40 respectively 41 Mistake.

1

Internal combustion engine

2

inlet side

3

outlet

4

air inlet

5

charging

6

compressor part

7

turbine part

8th

wave

9

air supply

10

intercooler

11

Charge air sensor

12

throttling device

13

impulse charger

14

fuel injector

15

intake valve

16

ignition device

17

outlet valve

18

combustion chamber

19

piston

20

knock sensor

21

temperature sensor

22

Tachometer

23

exhaust duct

24

Wastegate

25

exhaust pipe

26

Flow area

27

airflow

30

axial valve

31

rolling elements

32

Through opening

33

axial bore

34

first bearing ring

35

second bearing ring

36

bearing cage

37

Contact surface rolling element first bearing ring

38

Contact surface rolling element second bearing ring

39

Bearing ring segment

40

drilling Rolling element first bearing ring

41

drilling Rolling element second bearing ring

42

ring bearing cage

43

Clamping bearing cage 36

44

drive (Electric motor)

45

Pinion / friction wheel

46

Contact surface rotatable bearing ring

Claims (12)

Impulse loader for an internal combustion engine ( 1 ), the impulse charger ( 13 ) of the inlet side ( 2 ) of the internal combustion engine ( 1 ) and in an air supply ( 9 ) and the flow cross section ( 26 ) of the air supply ( 9 ) for the combustion air flow ( 27 ) at least partially releases or closes, characterized in that the impulse charger ( 13 ) as axial valve ( 30 ) is executed. Impulse charger according to claim 1, characterized in that the impulse charger ( 13 ) is designed as a modified thrust bearing. Impulse charger according to claim 2, characterized in that the thrust bearing a first bearing ring ( 34 ) and a second bearing ring ( 35 ), in each of which axial bores ( 33 ) are executed. Impulse charger according to claim 3, characterized in that one of the bearing rings ( 34 . 35 ) rotatably in the air supply ( 9 ) and the other La Gerring is rotatable relative to this. Impulse charger according to claim 3, characterized in that one of the bearing rings ( 34 . 35 ) is driven monotonously rotating. Impulse charger according to claim 3, characterized in that one of the bearing rings ( 34 . 35 ) is rotationally driven in an oscillating manner. Pulse loader according to claim 6, characterized in that the Drehwinkelauslenkung one of the bearing rings ( 34 . 35 ) is substantially 22.5 ° or less relative to the other. Impulse charger according to claim 3, characterized in that the axial bores ( 33 ) over the circumference of the bearing rings ( 34 . 35 ) are arranged evenly distributed. Impulse charger according to claims 2 and 3, characterized in that the thrust bearing a bearing cage ( 36 . 42 . 43 ), which with appropriate rotational position of the bearing rings ( 34 . 35 ) to each other the axial bores ( 36 ) closes and causes a pneumatic seal. Impulse charger according to claim 3, characterized in that one of the bearing rings ( 34 . 35 ) is driven about the common axis. Pulse loader according to claims 2 and 3, characterized in that at axial prestress of the bearing rings ( 34 . 35 ) a rolling movement of rolling elements ( 31 ) an alternating opening and closing of the axial bore ( 33 ) causes. Impulse charger according to claim 1, characterized in that the flow-through cross section ( 26 ) of the air supply ( 9 ) of the number of axial bores ( 33 ) in the bearing rings ( 34 . 35 ) is dependent.