EP1301704A1

EP1301704A1 - Fuel injection device for combustion engines

Info

Publication number: EP1301704A1
Application number: EP01964979A
Authority: EP
Inventors: Friedrich Boecking
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2000-07-06
Filing date: 2001-06-13
Publication date: 2003-04-16
Also published as: DE10032924A1; WO2002002931A1; US6575140B2; US20020170536A1; JP2004502089A

Abstract

The invention relates to a fuel injection device (1) for combustion engines comprising a high pressure fuel source (2) which enables fuel to be guided to a fuel injection opening (8) via a control valve (7). The control valve unit (7) consists of a valve body (11) and an actuator unit (10) which can be arranged (9) and displaced axially therein and which actuates the valve member (9). A first high pressure line (6) connected to the high pressure fuel source (2) flows into a first valve chamber (14) of the control valve unit (7). A first valve seat (13) is provided on an outer diameter of the valve body (11) between the first valve chamber (15) and a second valve chamber (15) which is connected to the injection opening (8) via a second high pressure line (23). A second valve seat (24) is formed on an inner diameter of the valve member (9). A locking device (25) engages with second valve seat.

Description

Fuel injection device for internal combustion engines

State of the art

The invention is based on a fuel injection device for internal combustion engines, in which a control valve unit for metered fuel injection is interposed in a fuel guide from a high-pressure fuel source to an injection opening. Such fuel injection devices known from practice, which are used in particular in common rail systems, control the supply of fuel to the injection opening, which is usually designed as a nozzle holder arrangement, generally via a slide valve or seat slide valve which can be balanced or partially balanced.

These slide valves or seat slide valves have control edges for releasing and covering feeds and discharges, whereby the usually small coverings result in large leakage fuel flows inside the slide valves, which adversely affects the injection of fuel into a combustion chamber Engine affects.

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Nem locking body and a locking element arranged between the locking body and the valve member has a self-centering, which is why only small requirements have to be made on the manufacturing tolerances.

Further advantages and advantageous embodiments of the invention result from the patent claims and from the exemplary embodiment described in principle below with reference to the drawing.

drawing

An embodiment of the invention is shown in the drawing and is explained in more detail in the following description. The single figure of the drawing shows a schematic representation of a fuel injection device according to the invention for internal combustion engines with a fuel guide from a high-pressure fuel accumulator, the construction of a control valve unit of the fuel injection device being shown in particular.

Description of the embodiment

The figure shows a fuel injection device 1 for internal combustion engines of motor vehicles, which is designed as a common rail injector for the injection of preferably diesel fuel. The common rail system comprises a high-pressure fuel source 2, which is designed with a high-pressure fuel reservoir 3. The high-pressure fuel reservoir 3 is supplied with fuel by a high-pressure fuel feed pump 4 from a fuel reservoir 5, which is compressed to the injection pressure. From the high-pressure fuel reservoir 3, a first high-pressure w to to p> H in o in o in o in

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annular groove-like shape 16 of the valve member 9 is formed.

A first guide 17 of the valve member 9 in the valve body 11, which has the same diameter as the outer valve seat 13, connects to the first valve chamber 14, in which there is permanent high pressure via the high-pressure line 6 during operation of the fuel injection device 1.

A first transmission piston 19 is arranged between the piezo-side end of the valve member 9 and a hydraulic chamber 18 serving as a hydraulic transmission, which transmits to the valve member 9 a change in length of the piezoelectric actuator 10, which is caused by a voltage applied to the piezoelectric actuator 10 ,

Between the piezoelectric actuator 10 and the hydraulic chamber 18, a second transmission piston 20 is provided which, with its end facing away from the piezoelectric actuator 10, dips into the hydraulic chamber 10. The hydraulic chamber 18 serves on the one hand as a transmission element for changes in length of the piezoelectric actuator 10 and on the other hand as a compensation element for temperature-related expansion fluctuations of the components surrounding it.

In the contact area between the first translation piston 19 and the valve member 9, an annular space 21 is provided around the valve member 9 or the first translation piston 19 in the valve body 11, from which a first leakage line 22 leads away.

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for guiding fuel from the area of the blocking device 25 into the leakage oil space 34 in the plate 26, through-bores 36 covering the drainage channel 33 are provided.

As shown in the figure, a further leakage line 38 is provided in the area between a second guide 37 and the drain channel 33 to relieve the control valve unit 7 or to discharge excess fuel from this area of the control valve unit 7, which is the relief side of the control valve unit 7 for the Represents leakage oil.

In the present embodiment, the second guide 37 is installed with a play that is greater by a factor 2 to 3 than the play of the first guide in order not to tension the system. Of course, in other embodiments, a different game, which is greater than the game of the first guide 17 by a factor of 2 to 5, for example, can also be provided, the first guide 17 having a game of preferably 1 micrometer to 4 micrometers and the second guide 37 can have a clearance of 4 microns to 10 microns.

The fuel injection device 1 according to the figure of the drawing works in the manner described below.

In the closed state of the injection opening 8, which means when the piezoelectric actuator 10 is not energized, the valve member 9 with the valve head 12 bears against the outer valve seat 13 and is loaded by the spring 32 with a spring preload. In this position of the valve member 9, there is no flow via the inner valve seat 24 Leakage oil, whereby the amount of leakage oil is kept very low.

High pressure from the high-pressure fuel source 2 is present in the first valve chamber 14 above the outer valve seat 13. To open the injection opening 8, the piezoelectric actuator 10 is subjected to voltage, which causes a sudden axial expansion of the piezoelectric actuator 10. The rapid actuation of the piezoelectric actuator 10 generates an actuating pressure or opening pressure in the hydraulic chamber 18, which is transmitted to the valve member 9 via the first transmission piston 19, the hydraulic chamber 18 and the second transmission piston 20. The translation of the transmission of the change in length of the piezoelectric actuator 10 is thus completely decoupled from the valve member 9.

Since the control valve unit 7 is only slightly compensated for partial force, i.e. designed to be almost force-balanced, it can be operated directly. To actuate the valve member 9, only the spring force of the spring 32 and a resultant force acting on the valve member 9 from the high pressure of the fuel have to be overcome via the piezoelectric actuator.

If the opening pressure built up by means of the piezoelectric actuator 10 is switched through to the valve member 9 via the hydraulic chamber 18, the first and second transmission pistons 19, 20 or an alternative mechanical transmission device and this is lifted from the outer valve seat 13, the latter flows under high pressure to the control valve unit 7 delivered fuel from the high-pressure line 5 via the first valve chamber 14 and the open outer valve seat 13 into the second valve chamber 15. ω w to to P> H in o in o in o in

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CQ P- rt td CQ ω 0 rt 53 P- P- tr 53 ω Pi i CQ P "0 0 53 Φ rt P- φ φ Ω PP φ Φ cn p- Φ P- φ rt 0 ¹ ii Φ 0 to Φ Φ Φ 0 Pi 0 H φ P-

CQ tr P ¹ 0 l 3 P- P ¹ P- ri P- Φ Pi 0 rr ü ri pr 0 Pi P. ω rr rt et CD CQ φ P = 0 CD CD 0 Pi 0 xj Ω φ P- H et CQ Pi 0 td P Φ 0

P o CQ P- tΛ 0 et P- - tr pr 0 = 53 P- 0 0 to P i Φ li 0 ω 3 0 pr φ Ω P. rt Φ Φ PP tr P- Hi rt 0 P- oo K Ω tr CQ rt ü Pi CQ tr P. ISl P- α P- tr CQ φ ii Pi ft) 0 Φ Hl tQ 0 ^{^} li CQ

Φ P Φ P ¹ Φ Pi 0 = rt P rt CQ φ H P. P- P- P ¹ Ω 53 CO 0 Φ Φ to r Hlü P- 3 P- tr to H Φ P "Φ Ω CQ P> CD tr P- rt φ 0 0 = u rt Ω Pi φ φ n 0 = Hi φ P. - Φ P- Φ Φ i Φ P- CQ et Hl

P- P • d tr P <J H rr 0 = P- P- α rt H P- 0 Pi 0 0 P- Hi

CQ 0 P- Φ IQ 0 53 Pi tr Φ P. tr rt Φ P- 0 Φ 0 0 Φ φ ω P ¹ 0 53 et CD φ ü φ P- 0 N »i P- H 0 Ω 0 ω Ω Φ> P. li o CQ Φ φ

• CQ ISl tr P- φ l 53 Φ et 0 W 0- CQ CQ pr pr P- <! ISl P "rt φ 0 P Φ P- rt 0 Ω ^* CQ CQ P rt Φ 0 et φ Φ 0 P P- Φ Ω

CQ P 0 P- φ Φ tr P- Φ 0 53 P- 0 P- H 0 0 <! 0 Φ 0 - tr CD IΛ> CQ H Pi 0 53 ω P = P- Φ 0 CQ P m rt φ P. φ

P- Q CQ rt Φ Φ Er P. φ PPO 00 ii CD 53 ¹ 0 rt "d P- H P. LSI

Ω Φ φ 0 P ⁱ P- CQ 0 0 P. φ pr P- Pi HOPP "φ VD 0 N ^J 53 rr 0 P. FP Φ ffi Ml 0 0> ii φ 0 = li 0 Φ P: 3 CD 0

Φ P P- er Φ Φ 0 Tj ü Φ ω 0 0 H 0 CQ I P- CQ 3 rt i

0 0 H Φ 0 Ω Ml φ 53 Φ Ω Ω P ¹ CQ tΛ CQ 0 CO P- P

P. 1 pr pr 1 P- P- tr pr Φ P- MP ¹ 1 P- rt 0 rt 1 PP l 0 PP 0 P • <; P- o tQ P-

Φ 1 1 P. 1 1 0 ¹ CQ 1 ¹ φ

In an embodiment of the control valve unit that differs from the present exemplary embodiment, it can of course also be provided that the valve member with its piezo-side end is connected directly to the hydraulic chamber or is immersed in it without the interposition of a first transmission piston and thus acts directly on the control pressure via the hydraulic chamber becomes.

Claims

Expectations

1. Fuel injection device (1) for internal combustion engines with a high-pressure fuel source (2), from which fuel is guided to an injection opening (8) via a control valve unit (7), the control valve unit (7) having a valve body (11), one axially displaceable in the latter Arranged valve member (9) and an actuator unit (10) actuating the valve member (9), a first high-pressure line (6) connected to the high-pressure fuel source (2) opening into a first valve chamber (11) of the control valve unit (7) , and a first valve seat (13) is provided on an outer diameter of the valve body (11) between the first valve chamber (15) and a second valve chamber (15) connected to the injection opening (8) via a second high-pressure line (23) , and wherein a second valve seat (24) is formed on an inner diameter of the valve member (9), in which a locking device (25) engages.

2. Fuel injection device according to claim 1, characterized in that the valve body (11) is integrally formed at least in the region of the valve member (9).

3. Fuel injection device according to claim 1 or 2, characterized in that the locking device (25) on the actuator unit (10) facing away from the valve member (9) is arranged and is preferably formed with an at least approximately spherical closing element.

4. Fuel injection device according to claim 3, characterized in that the locking device (25) has a locking body (28) formed from a plate (26) and a pin (27), the closing element (29) between the pin (27) and the Valve member (9) is arranged and is flattened on its side facing the pin (27).

5. Fuel injection device according to claim 4, characterized in that the closing element (29) interacts with an at least approximately conical end region of a bore (30) of the valve member (9) which is provided via at least one channel (9) provided in the valve member (9). 31) is connected to the second valve chamber (15).

6. Fuel injection device according to one of claims 4 or 5, characterized in that between the plate (26) of the locking body (28) and the valve member (9) a spring (32) is arranged, the plate (26) with its the piezoelectric Unit (10) facing away from the valve body (11) and the pin

(26) of the blocking body (28) extends from the plate (26) in the direction of the valve member (9), an outer The outer diameter of the plate (26) in the area of the locking device (25) is smaller than the inner diameter of the valve body (11).

7. Fuel injection device according to claim 6, characterized in that the valve body (11) in the region of the contact surface of the plate (26) has at least one drain channel (33) which is covered by the plate (26), and in the plate (26) at least one passage bore (36) is provided which overlaps the outlet channel (33).

8. Fuel injection device according to one of claims 1 to 7, characterized in that the first valve chamber (14) of a between the valve body (11) and the valve member (9) formed first guide (17) of the valve member (9) in the Valve body (11) and the first valve seat (13) is limited, the first guide (17) being provided between the actuator unit (10) and the first valve chamber (14).

9. Fuel injection device according to claim 8, characterized in that an annular space (21) is provided on the side of the first guide (17) facing the actuator unit (10), from which a first leakage line (22) branches off.

10. Fuel injection device according to one of claims 1 to 9, characterized in that the second valve r by (15) of the second valve seat (13), the valve member (9) and the valve body (11) is limited, the second Valve chamber (15) to the first valve chamber (14) on the side of the outer valve seat (13) facing away from the piezoelectric unit (10).

11. Fuel injection device according to claim 10, characterized in that a further leakage line (38) is provided in the region between the second guide (37) of the valve member (9) and the drain channel (33).

12. Fuel injection device according to one of claims 1 to 11, characterized in that the actuator unit is designed as a piezoelectric unit (10) which actuates the valve member (9) preferably via a hydraulic chamber (18), the hydraulic chamber

(18) a first transmission piston (19) is connected upstream and the valve member (9) with its end facing the piezoelectric unit (10) is operatively connected to the hydraulic chamber (18) via a second transmission piston (20).

13. Fuel injection device according to one of claims 1 to 12, characterized in that the high-pressure fuel source (2) is designed as a common rail system and the fuel injection device (1) is a pressure-controlled common rail system.