EP1364114A2 - Fluid dosing device with a throttle point - Google Patents

Abstract

The invention relates to a fluid dosing device for a pressurized liquid, comprising a chamber (35) which is arranged in a housing (3) and which is supplied with pressurized liquid by means of a liquid supply line (17, 19); in addition to a valve needle (9) which is guided through the chamber (35), the first end section of said valve needle being able to be lifted and the second end section thereof forming a valve which is connected to the chamber (35), in conjunction with a valve seat disposed on the housing (3). In order to provide a tight and enduring leadthrough for the valve needle, metal bellows (33) are provided as a leadthrough element for the first end section of the valve needle (9) when seen from the chamber (35) in an outward direction. The metal bellows seal the chamber in said region in a tight manner. A throttle point (37, 39) is provided between the valve needle (9) and the inner wall of the chamber between the metal bellows (33) and the mouth (18) of the liquid supply line (17) leading into the chamber.

Description

description

Fluid metering device with throttle

The present invention relates to a fluid metering device for a pressurized fluid with a chamber located in a housing, to which the pressurized fluid is supplied through a fluid supply line, and with a valve needle guided through the chamber, the first end section of which outside the chamber with a stroke can be acted upon and the second end section of which forms a valve connected to the chamber with a valve seat provided on the housing.

In the prior art, various sealing or

Feedthrough elements for fluid metering devices are known. For the application of dosing pressurized fuel with a pressure of up to, for example, 300 bar and a working temperature of -40 ° C to + 150 ° C, special requirements are placed on a product suitable for series production. In particular, high requirements regarding embrittlement, wear and reliability have to be met. The fatigue strength of previously used O-ring seals does not meet the above requirements. Instead of O-rings, membrane seals such as Metal beads or similar be used. When using such membranes as a lead-through element of a valve needle through a pressurized chamber, however, the requirements with regard to a high degree of axial compliance and at the same time sufficient pressure resistance cannot be met.

Similar to diesel injectors, the valve needle can also be made by fitting the needle to play in a cylindrical housing bore. The disadvantage here is the unavoidable leakage along the needle feedthrough. By the greater hydraulic losses also reduce the overall efficiency of the engine.

The object of the present invention is to provide, in particular, a tight passage of the valve needle in a generic fluid metering device, which achieves the required fatigue strength.

According to the invention, this is achieved in a fluid metering device according to the preamble of claim 1 in that at least one throttle point is provided circumferentially between the valve needle and the chamber inner wall in the chamber section between the lead-through element and the opening of the fluid supply line into the chamber. Measurements have shown that metal bellows designed as lead-through elements for use in high-pressure injection valves, for example in automotive engineering, can easily withstand static pressure loads of up to approx. 200 bar. By increasing the wall thickness, a much higher compressive strength can also be achieved. Further investigations on moving metal bellows seals also showed that a metal bellows subjected to high pressure does not suffer any degradation when an axial movement of up to 50 μm typical for the injection valves is carried out with a frequency of 50 Hz. By using a metal bellows, the fuel chamber is hermetically sealed with sufficient pressure resistance.

However, it was surprisingly found that the metal bellows fail after only 10 minutes when used in a high-pressure injection valve under a static pressure load of 200 bar. This is due to the fact that when the injection valve or injector is opened and closed, pressure waves are triggered in the fuel chamber of the injector, which, depending on the opening and closing times of the injector, have an amplitude of up to ± 50% of the set fuel pressure and one frequency of approx. 500 Hz - 10 kHz, typically in the range of approx. 500 - 800 Hz, swing around the set basic pressure. The occurrence of such pressure oscillations leads to failure of the metal bellows seal when pressure waves are triggered. The throttle points provided according to the invention protect the metal bellows from the destructive effect of these pressure oscillations.

In summary, according to the invention, a sufficient tightness of the fuel chamber is realized by the metal bellows, the metal bellows seal being protected from the pressure waves occurring during operation, thereby achieving a durability characteristic of at least 10 ⁹ load cycles (approx. 2000 operating hours) that is typical of motor vehicles

The metal bellows advantageously has a wall thickness of 25 to 500 μm. These small wall thicknesses have proven to be completely sufficient at high pressures of, for example, 300 bar. Experiments have shown that forming the metal bellows in the form of semi-circle segments, which are visible in the longitudinal section, has particular advantages. These semi-circular segments can be supplemented by straight sections in between.

According to a preferred embodiment it is provided that the elastic bushing element is fastened to a mounting sleeve, in particular by a welded connection. This is particularly favorable in terms of production technology, since in particular a metal bellows can only be attached directly to the valve needle with comparatively great effort. The mounting sleeve also provides an element that can be used to easily implement a precisely dimensioned throttle point in the fuel chamber.

In order to be able to provide a suitable throttle point in the fuel chamber, an upper guide sleeve is an alternative or in addition to the appropriately dimensioned mounting sleeve formed in such a way that a narrow and longest possible clearance fit is realized by this valve needle guide. Since the upper valve needle guide is already provided in the fuel injector, additional components can be omitted.

If both throttling points - "assembly sleeve" and "upper valve needle guide" - are implemented simultaneously in the fluid metering device, the respective throttling gaps can be made larger and / or shorter in the axial direction without negatively affecting the protective effect of the throttling points for the metal bellows. In addition, mismatches that could lead to a pinching of the valve needle can be avoided. However, this also applies if the throttle point formed by the mounting sleeves is dispensed with, the throttle point formed by the upper guide sleeve having to be designed accordingly.

In order to be able to prevent or severely restrict the propagation of the pressure waves in the fuel chamber in the direction of the metal bellows, the free cross section between the valve needle and the chamber inner wall has been changed abruptly in the region of the throttle point. This leads to the desired reflection of the pressure waves at the chamber inner wall section extending transversely to the direction of propagation of the pressure waves.

The gap width of the throttle point is selected depending on the position of the throttle point in the fuel chamber and the length of the throttle gap, taking into account the static and dynamic pressure conditions. A few m have resulted as a typical value for the gap width of the throttle point in the fuel chamber of a high-pressure fuel injector.

Four exemplary embodiments of the fluid metering device according to the invention are described below using schematic representations. Show it: La in a longitudinal section the first embodiment of the fluid metering device,

Fig. Lb two cross-sectional views along the lines A-A and B-B in Fig. La,

2 in a longitudinal section the second embodiment,

Fig. 3a in a longitudinal section, the third embodiment of the fluid metering device, and

3b shows two cross-sectional representations along the lines A-A and B-B in FIG. 3a.

In an injection valve 1 shown schematically in FIG. 1 a, b according to a first exemplary embodiment, the actuator unit, which is generally known per se, is not shown for reasons of simplification. The fuel injection valve 1 has a housing 3 with a central bore, in which a valve body 5 is mounted. A valve needle 9 is guided axially displaceably in a valve body bore 7 of the valve body. For this purpose, a lower or front and an upper or rear guide sleeve 11, 13, which form corresponding valve needle guides, are fastened in the valve body bore 7 at their lower and upper end section on the valve body 5. The constrictions realized thereby are designed so that they do not hinder or restrict a flow of liquid when the valve 1 is opened and closed. For this purpose, the valve needle 9 is provided with a rounded square cross-section according to FIGS. The valve needle 9 with the rounded edge regions 14 is fitted into the two guide sleeves 11, 13 with a play of less than 2 μm. The free gap between the four side surfaces of the square of the valve needle 9 and the cylindrical inner wall of the guide sleeves 11, 13 is designed to be significantly larger in order to avoid any throttling effect.

In the basic state, a valve plate 15 formed on the front end section of the valve needle 9 closes a valve seat 16 on the valve body 5. In the valve body, a valve body fuel feed line 17 is provided, which is seen in axial extension between the lower and the upper guide sleeve 11, 13 with an opening 19 in the valve body bore 7 opens. Correspondingly, a housing fuel feed line 21 is also provided in the valve housing 3. At the upper end portion of the valve needle 9, a spring plate 23 is attached to this. A nozzle spring 25, which is supported on the housing side and thereby prestresses the valve needle 9 in the closing direction, presses on this. Above the upper guide sleeve 13 is in the

Central bore of the valve housing 3 an outer mounting sleeve 27 attached. The outer mounting sleeve 27 has at the lower end a sleeve collar 44 which rests on an annular bearing surface 45 on the housing 3. The sleeve collar has an outer surface 46 which is arranged on an inner wall 47 of the housing 3. A sealing element 48 in the form of a sealing ring is inserted between the outer surface 46 and the inner wall 47. The sleeve collar 44 is welded tightly to the inner wall 47 with an annular circumferential weld seam 49. Through an opening in a sleeve base 29, this forms a needle bushing which is sealed as described below. In a partial section of the outer mounting sleeve 27 which extends in the axial direction to a limited extent, its inner wall forms a constriction, described in more detail below, with the outer wall of an inner mounting sleeve 31, which in turn is fastened to the valve needle 9. A cylindrical metal bellows 33, through which the valve needle 9 is guided to the outside, is welded to the outer and inner mounting sleeves 27, 31. The metal bellows 33 is used to hermetically seal the fuel chamber 35 from an unpressurized, air-filled intermediate space 36. The metal bellows 33 is preferably in the region of the opening

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1

Mounting sleeve 27, 31 chosen so small and long that a sufficient throttling effect is realized. Due to the small distance between the inner and outer mounting sleeves 27, 31, the pressure waves triggered in the fuel chamber 35 when the valve 1 is opened and closed cannot or only slightly act on the metal bellows 33.

A fuel injection valve 1 according to the third exemplary embodiment shown in FIGS. 3a, b alternatively has a second throttle point 39 in the region of the upper valve needle guide or the upper guide sleeve 13 instead of the first throttle point according to the first two exemplary embodiments. Since the fuel feed line 17 opens below the upper valve needle guide 13 into the space between the valve needle 9 and the valve body 5 or the fuel chamber 35, the fuel to be injected into it does not pass through the upper valve needle guide 13. Therefore, the upper valve needle guide itself can be designed as a narrow, long cylindrical clearance fit of the valve needle 9 in the upper guide sleeve 13, as shown in section BB in FIG. 3b. In contrast to the lower valve needle guide (section AA), the valve needle 9 is not designed as a square, but rather cylindrical (section BB). At this second throttling point 39, the pressure waves triggered during opening and closing processes are reflected and a dynamic volume exchange in the direction of the metal bellows 33 is strongly throttled. Multiple fits can also be avoided by integrating the throttle point 39 in the valve needle guide. The throttling action of the upper valve needle guide 13 separates the fuel chamber 35 into two partial volumes, namely a first and a second chamber partial volume 41, 43. Although dynamic pressure changes with a large amplitude can be generated in the lower first partial volume 41 of the fuel chamber 35 by opening and closing the injection nozzle these are greatly weakened by the dynamic sealing effect of the second throttle point 39 in the upper second partial volume 43 of the fuel chamber 35, in which the metal bellows oo M IV> P ¹ cn o cn o Cn o Cn

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Φ tr Ό φ tr P P 'P' Φ Ω CL CL H P d Φ φ er ω Φ rt H P- o- rt EP r

P- rt O: H α P rt d 3 o 3 CL 3 t φ P- PPHPP CL Φ φ P ¹ N Φ CL

P> • Hl P- φ o Φ P ^J φ Φ Φ s: li Φ P ^ IQ P \ -> σ P- co <P. H d φ Hi Ω 3 iJ P- cn d cn H P- Φ d cn lJ K d tr φ O d ι-J Φ Φ tj t α P tr fi ^¬ Φ CL cn cn 3 ω P P- P- K P- P φ? rt Φ ij Φ HP Φ iQ P 3 CL Ω

Φ Φ rt tr el) cn P Ω φ φ Φ EP P d = cn cn P ¹ P cn Ω cn o O CL P Φ rt "<tr i HP * <P- cn tr PH Φ? Rt P rt rt Φ P tr Ω tr cn P ^J N P- <! P Hi o Q- P "M cn cn PP. φ ω cn 3 PO tr Hl tr Φ cn CL P- Φ P- P d:

P s CL s: tj tr P- £ CL rt P lJ Φ <! rt φ P Φ d: HH φ P- cn P- cn φ 3 tr cn Φ Φ PPP CL P- CL o φ P- P φ OOPP cn tr P- Φ P "φ p- KQ H P- lJ rt rt cn P- d Hi cn φ H Φ cn P ¹ P cn H Hi rt d φ Ω j Φ cn φ rt. -. Rt cn d

DJ P rt> Ü ι-JTH φ P CL P- N Hi Φ Ω I- ¹ tr d er <rt p: H Φ P Φ Ω P

PM p- H cn P- g P dd P d 1 P tr P lJ P Φ Φ Φ d rt P P- P tr ιQ rt P ¹ P- cn ω P- P- ü P CΛ P φ CL HP ιQ cn P - IQ PP EP. Ω φ er P o Ω cn rt lJ 3 OK rt Φ Ω α cn O s; er rt φ cn Φ rt P ^J Φ σ tr P er lJ P ω tr rt N d φ P- Φ PP "tr Φ s: CL P- Φ p- tr Φ P P- Φ H α ι- (rt d Φ d Ό <Ω P φ cn p: P Φ Φ φ P- ω Φ P ¹ Φ P- o ω α Hi

Ω ιQ H Φ s: Φ Φ K rt Ω CL d rt P- ι-J Ω P Φ> P ω φ ω * Q Hi H P-

W P- H P- cn P ö Ό Φ er P- EP cn cn N P tr. 3 d P Kß S cn Φ d = d P er O rt l-J rt P- d P P P- φ Φ Ό φ Q • P Φ φ cn α o φ φ N tr Ω CL

Φ ON α P- 3 ti cn P- H- ¹ 3 H tj dw CL 3 Ö P Hl Φ p- P li Φ ii fr φ

<JH cn s- P ¹ Ω cn rt fQ S Φ φ P 3 • φ P- rt d: - ¹ cn rt cn cn P- dp: rt

DJ P- Φ d P φ cn N Ϊ7 ¹ d cn PP Ω d 3 ti σ φ tr Hi rt P rt rt Ω PP. cn cn P Ω 3 P Ξ 3 P s Φ tr tr cn P- φ φ d Φ tj d: ιQ Φ Φ rt ιQ rt rt rt - φ PP φ Φ ιQ Φ co li P ¹ tr lJ o KQ os Φ P- PHW P- d tr CL Φ - ω Φ α d P- P er P- cn P £ d ^; P Ω ti PPH d tr α er HP

P CL P- α cn rt cn ιQ α CL P CL φ P ¹ φ tr Hl vCj d H d = H Φ ω Φ d 3 QP cn 3 ö Φ P- Φ Φ H Φ CL Φ Φ rt rt ω HHH, P - cn P Ω o P P- P- P P-

P d i-J P P ti O: P φ P- cn P CL P φ rt p: P P tr iQ tr cn ω P cn iQ rt

DJ P P- N li "EP. H Ω KQ Φ P ¹ S Φ tr CL P" φ φ cn O CL Ό Φ d 3 s: Ω σ rt Pi a. Φ tr σ Φ 3 P- ¹ φ Φ PH d fi ^¬ P- "3 CL φ l P- P p- cn P- Φ tr d P Φ li α σ d tr p- 3 d P el) cn Φ P- N) (- CL φ cn QP S. P- 3 H _— »3 cn d lJ N ti d: er tr PP ιQ P Ό tr φ _^ cn P- P ^J ιQ rt

Φ Φ rt Φ Ω tr 3 _ -. ti dd Ω _- • Φ φ vQ H o iQ tr P- P- "> rt co φ Φ cn P cn Φ cn tr" N φ S er o Ω 3 ff cn cn H Φ PP cn P- P φ o Φ KΩ φ cn φ P ¹ Φ P cn 3 s: H Φ N tr ^ 3 φ Ω ιQ cn P φ cn er o P- P- Ω φ rt P "P Φ φ. Rt rt s: tr φ tr Φ Φ φ rt ιQ Φ Φ Φ P ^> l- ¹ ιQ PP 'tr t

N φ rt i H cn Φ P • M P- ^ <cn) H cn rt o φ P rt H φ Φ Φ d-- rt PP "P cn P P- P- 3 C cn -j P- rt N CL P 3 P- • Φ iQ 3 CL cn rt

, P- 3 CL φ PP ^J -> ^ P lJ Φ φ Φ rt φ ω φ Φ P s: Φ co φ φ N s φ tu Ω 3 Φ H cn <! tr cn NPH tr P- H rt P CL d ^ er -J P- P Pi rt ft φ tr φ cn rt OP Φ rt £ d cn co Φ P ^J s: P- rt O ^ jd = P- PH. P rt Φ H CL Φ P "P- Φ Φ P ^J P> P rt Φ cn OO CL tr P- cn ^ P

HP rt S φ P- g ιQ P P- ¹ P- P- CL Φ • H P- Ω er tr H Φ H CL cn P P- Hi P "

P- Φ φ lJ KQ 3 cn φ t- ^J rt ω Φ <! P CL P tr Φ 3 d φ rt 3 iQ rt er φ; P- rt et Φ jd Φ Ω H φ a Φ φ Φ cn PPP rt d ω P er o P ^J P CΛ - P o - PP tr H £ P- PHP Ω P- φ iQ CL p- H rt P ¹ cn P <• ö • o ιQ CΛ Φ Φ. tr Ω P- cn cn dd P Φ 0 ιQ

N cn o P "P- .t» P _ ^ £ O rt Φ α H tr P tr PHP Hi d rt er Φ ω o SP "P P- P- Φ PS ö <dp: rt φ φ d = CL Ω φ Hi co cn P d P Φ P- cn φ 3 H φ er P- "Φ P- P li P cn tr P- P ¹ Φ co rt P 3 P ¹ Ό cn er tj cn 3 Ϊ P" rt φ cn Ω \ x? PP cn CL P P- p: rt Φ ιQ PO Φ CL CL Φ cn Ό er & rt tr rt d S cn Φ P- CL φ er P iQ

PP cn cn P P- Φ HPP o P n P- 1 _^ Hi φ rt φ p- 3 N l Φ

CL 1 1 3 Φ 3 1 3 cn CL P ¹ P 1 1 P- P »Φ s: 1

Φ .fe co tj φ 1 Φ ^ P 1 co

P co o 1 P l-J

Claims

claims 1. Fluid metering device for a pressurized fluid with a chamber (35) located in a housing (3), which is pressurized by a fluid supply line (17, 21) Fluid is supplied, and with a valve needle (9) guided through the chamber (35), the first end section of which can be acted upon by a stroke outside the chamber and the second end section of which is connected to the chamber with a valve seat (16) provided on the housing (3) (35) forms a connected valve, an elastic feed-through element (33) for the first end section of the valve needle (9) from the chamber (35) to the outside, which seals the chamber in this area, characterized in that it is circumferential At least one throttle point (37, 39) is provided between the valve needle (9) and the chamber channel wall in the chamber section between the bushing element (33) and the mouth (19) of the fluid supply line (17) into the chamber (35). 2. The fluid metering device according to claim 1, wherein the bellows, in particular a metal bellows (33), is provided as the lead-through element. 3. The fluid metering device as claimed in claim 2, so that the metal bellows (33) has a wall thickness of 25 to 500 μm. 4. Fluid metering device according to claim 1 to 3, characterized in that the bushing element (33) is attached to a mounting sleeve (31), in particular by a welded connection. 5. Fluid metering device according to claim 4, so that the throttle point (37) is formed in the chamber (35) by the mounting sleeve (31). 6. Fluid dosing device according to one of the preceding claims, that a top valve needle guide (13) is provided, and that the throttle point (39) is formed in the chamber (35) by the top valve needle guide. 7. Fluid metering device according to one of the preceding claims, that the free cross-section between the valve needle (9) and the chamber inner wall is changed abruptly in the region of the throttle point (37, 39). 8. Fluid metering device according to one of the preceding claims, that the gap in the region of the throttle point (37, 39) is a few μm wide. 9. Fluid metering device according to one of the preceding claims, that the fuel is used as the fluid, and that the fuel pressure is in the range from 1 to 500 bar. 10. Fluid metering device according to one of the preceding claims, characterized in that that the diameter of a clearance fit of the valve needle (9) corresponds to a hydraulically effective diameter of the metal bellows (33).