EP0960274A1

EP0960274A1 - Fuel injection device for internal combustion engines

Info

Publication number: EP0960274A1
Application number: EP98928124A
Authority: EP
Inventors: Friedrich Boecking
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 1997-09-24
Filing date: 1998-04-03
Publication date: 1999-12-01
Anticipated expiration: 2018-04-03
Also published as: CN1241244A; EP0960274B1; JP2001505976A; CN1104556C; DE59807067D1; KR20000069080A; US6067955A; WO1999015783A1; DE19742073A1

Abstract

The present invention relates to a fuel injection device for internal combustion engines, wherein the opening and closing movement of a fuel injection valve (1) is controlled by the pressure in pressure chamber (9) acting on a pressure shoulder (16). The pressurised fluid supply to the pressure chamber (9) is controlled by a control valve member (23) which is displaced by the pressure in a working chamber (31). The pressure in said working chamber (31) is controlled by a pilot valve (55) having a closing body (56) which is displaced by a piezo drive (73) from a second valve seat (64) to a first valve seat (60), thus opening for a short moment the expansion duct (50) of said working chamber (31). The control valve member (23) is then opened and high-pressure fuel is supplied to the pressure chamber (9) for injection, which results in a very small pre-injection amount. In order to obtain the main injection amount, the closing body (56) is placed in a central position between the two valve seats (64, 60), thus establishing a longer connection for supplying the high-pressure fuel flow to the pressure chamber (9).

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 according to the preamble of claim 1. In such a fuel injection device known from EP 0 657 642, the high-pressure fuel source consists of a high-pressure fuel pump which conveys fuel from a low-pressure space into a high-pressure collection space, which communicates with the individual in the

Combustion chamber of the injection valves projecting to be supplied to the internal combustion engine is connected, the common pressure storage system (common rail) being kept at a certain pressure level by a pressure control device. To control the injection times and injection quantities, an electrically controlled control valve is provided on the injection valves, which controls the high-pressure fuel injection when it is opened and closed. The control valve in the known fuel injection device is designed as a 3/2-way valve, one on the

Injection opening of the respective injection valve opening pressure channel with the discharge from the high pressure source Injection line or connects to a relief line in a low pressure room.

Since the 3/2-way control valve in the known fuel injection device is actuated directly by the actuator of an electromagnet, the known fuel injection device has the disadvantage that the stroke of the valve member of the 3/2-way control valve and thus the control effectiveness of the valve is limited . With the well-known Kaftstoffein injectioneinrichtung it is because of

Using an electromagnet is particularly difficult to achieve a high switching speed of the control valve, especially if this device is to be used to inject a small pre-injection quantity and then a large main injection quantity via the fuel injection valve, thus opening and closing the control valve twice for this process must become.

Advantages of the invention

The fuel injection device for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that a large passage cross-section can be realized with the help of the control valve, which enables quick opening and closing of the injection valve member and a small-sized electrically controlled pilot valve is used to use the large Control valve providing passage cross sections. Because a piezo drive is also used to actuate the valve member of the pilot valve, an increased switching speed can be achieved. An increase in Switching speed moreover results for the realization of a pilot injection from the measure that the pilot valve has two valve seats which are arranged in the course of the relief duct of the working space and which are opened and closed alternately with a single actuation of the pilot valve member. Thus, with a single excitation of the piezo drive, an intermediate relief of the is without loss of time through a field build-up in an electromagnet or field degradation and without the high energy requirement that would otherwise be required

Achieved work space, which is only determined by the path that the pilot valve member must travel and the actuating speed of the piezo drive. In conjunction with the very large cross-section that can be controlled by the control valve, this enables the control valve to be switched very quickly and control correspondingly short injection quantities. Due to the property of the piezo drive with its actuator that it can assume a different position between the valve seats, the main injection quantity can also be controlled in a highly precise manner.

drawing

An embodiment of the invention is shown in the drawing and is explained in more detail in the following description. FIG. 1 shows an overall representation of the invention and FIG. 2 shows a partial enlargement of the representation of FIG. 1

Description of the embodiment The fuel injection valve 1 shown in FIG. 1 has a fuel injection valve member 2, which is guided with a guide part 3 in a bore 4 of a fuel injection valve housing 5. At one end of the fuel injection valve member, this has a sealing surface 6, which can be brought to bear on a valve seat 7 on the housing and thereby separates fuel injection openings 8 from a pressure chamber 9, which in the form of an annular space 10 extends around the end of the fuel injection valve member 2 to extends to the valve seat 7. The pressure chamber 9 can be connected to a fuel high pressure source 13 via a pressure channel 12 and a control valve 15. Fuel that is brought to injection pressure is constantly available in the high-pressure fuel source.

In the area of the pressure chamber 9, the injection valve member has a pressure shoulder 16, via which it can be lifted from the valve seat 7 for the purpose of injection when pressure is applied in the pressure chamber 9 against a closing spring 17 acting on the rear of the fuel injection valve member 2. The rear space 18 receiving the closing spring 7 is relieved of pressure via a relief channel 19.

On the other hand, the space 18 is delimited by an end piston 21 of a control valve member 23 arranged coaxially to the fuel injection valve member. This is part of a control valve 24, which is designed as a 3/2 way valve. The control valve member 23 is guided in a stepped bore, the part 26 of which is smaller in diameter also accommodates the space 18 and tightly guides the end piston 21 and whose larger part 27 has a piston part 28 of the control valve member 23. The piston part 28 delimits a working space 31 in the fuel injection valve housing with its end face 29 and is on its end face 29 away from the side provided with a tapered first sealing surface 32 which tapers to a diameter reduction 34. The narrowing of the diameter 34 then merges conically into the end of the end piston 21 facing away from the pressure chamber 18, forming a control edge 46. The first sealing surface 32 cooperates with a first valve seat 36 formed at the transition from the stepped bore part 27 with the larger diameter to the stepped bore part 26 with the smaller diameter. An adjustment of the control valve member 23 in the other direction is limited by the abutment of its end face 29 on a wall 75 which closes off the working space 31 on the opposite side.

In the area between the end face 29 and the first sealing surface 32, the piston part 28 has an annular constriction 38 and delimits an annular space 39 there, which is formed together with an inner recess of the stepped bore part 27, which is larger in diameter, following the first valve seat 36 and which is continuous is connected to the high-pressure fuel source 13 via a pressure line 40. Provided in the piston part 28 is a channel 41 which runs obliquely to the longitudinal axis of the control valve member 23 and which connects the constriction 38 to the working space 31 and which has a diameter limitation 42 on the side of the working space 31, which limits the inflow of pressure medium formed by fuel from the high-pressure fuel source into the Working space 31 throttles or its inflow rate is limited.

In the stepped bore part 26, which is smaller in diameter, an annular space 45 is formed between the wall of the stepped bore and the diameter reduction 34 on the control valve member 23, into which the pressure channel 12 opens. An inner recess 44 is also provided in the wall of the stepped bore part 26 with a limiting edge 49 oriented towards the valve seat 36, which together with the control edge 46 of the end piston 21 forms a slide valve. Furthermore, a flattened portion 47 is provided on the end piston, which together with the wall of the stepped bore part 26, which is smaller in diameter, forms a flow cross-section which is constantly open to the space 18. To the side of the annular space 45, the flattening is delimited by a horizontal edge 48 which lies in such a way that in the position of the control valve member 23 shown in FIG. 2 with the first sealing surface 32 resting on the first valve seat 36, a connection between the space 18 via the flattening 47 to the inner recess 44 and thus further via the pressure channel 12 to the pressure chamber. The pressure chamber 9 is relieved in this position of the valve member 23. This connection is only closed when the first sealing surface 32 during an axial displacement of the

Control valve member 23 has lifted from the first valve seat, this stroke being limited by the abutment of the end face 29 on the closing wall 75. In the course of this movement, the control edge 46 passes over the boundary edge 49 and, in the function as a slide valve, closes the connection between the inner recess 44 and the annular space 45. Up to this position, the edge 48 of the flattening always remains below the control edge 46, so that there is no connection between the space 18 and the annular space 45 results and in this position the fuel directed from the high-pressure fuel source to the pressure space 9 is not released to the space 18.

The work space 31 can be relieved via a relief line 50 which leads axially away from the work space 31 and has a diameter limitation 51 which limits a discharge rate. The relief channel opens into a valve chamber 53 of a pilot valve 55. A closing body 56 is one in the valve chamber 53 Adjustable valve member 54 of the pilot valve 55, which closing body 56 is located at the end of a plunger 57 which is guided in a guide bore 58 in the fuel injection valve housing 5. At the entry of the relief channel 50 into the valve chamber 53 there is a first valve seat 60 of the pilot valve, with which a first sealing surface 61 comes into contact with the closing body 56 in a first displacement position of the closing body 56 and closes the outflow through the relief channel 50. On the side of the closing body 56 opposite the first sealing surface 61, the latter has a second sealing surface 62 which merges into an annular groove 63 on the side of the tappet 57. This annular groove delimits in the guide bore 58, which opens into the valve chamber 53 via a second valve seat 64, an annular chamber 65 which is permanently connected to a further part 66 of the relief channel 50. In a second position of the closing body 56, the second sealing surface 62, which is in contact with the second valve seat 64, has interrupted the connection of the relief line 50 from the valve chamber 53 to the further part 66 of the relief line.

The closing body 56 is acted upon by a positioning force in the form of a compression spring 68 in the closing direction with its second sealing surface 62 bearing on the second valve seat 64. For this purpose, the compression spring 68 is clamped between the housing of the fuel injection valve and a spring plate 69 on the tappet 57. A further piston 70 acts on the plunger 67, which, at its other end, delimits a hydraulic chamber 71, which on the other hand is delimited by an actuating piston 72, which is part of a piezo drive 73, which is not shown here. Care is taken that the hydraulic space 61 is always filled. It serves for the Translation in such a way that the footprint of the actuating piston 72 is larger in cross section than the footprint of the further piston 70, so that a small adjustment path of the actuating piston 72 causes a large adjustment path of the additional piston 70 and accordingly a large opening stroke of the closing body 56 can be achieved . In particular, this ensures that the closing body 56 can move from the second valve seat 64 to the first valve seat 60 and that the relief line is sealed in both positions. The piezo drive also makes it possible for the closing body 56 to remain in a middle position in which the flow through both valve seats 60 and 64 remains open and thus a permanent relief of the working space 31 can be set via the relief line 50.

The fuel injector described works as follows: In the position of the closing body 56 shown, the relief line 50 is closed. In this case, fuel that is brought to the injection pressure can reach the working space 31 from the high-pressure fuel reservoir 13 via the annular space 39, the channel 41 and the constriction 42 and can likewise build up a pressure there that corresponds to the pressure in the high-pressure fuel reservoir. This causes the control valve member 23 to remain in the position shown, in which the first sealing surface 32 abuts the first valve seat 36 and thus a connection between the annular space 39 and the annular space 45 is prevented. Thus, no high-pressure fuel can get from the pressure line 40 via the pressure channel 12 into the pressure chamber 9 and bring the fuel injection valve member 2 into the open position. In this case there is no injection; the injection valve member 2 is in the closing position under the action of the restoring force in the form of the clamped compression spring 17. Position held. In order to trigger a fuel injection, the piezo drive 73 is now excited and lifts the closing body 56 from the second valve seat 64, so that the work space 31 is relieved. This causes the control valve member 23 under the action of a restoring force which, for. B. a pressure shoulder loaded by the fuel pressure on the closing member or a spring (not shown further) is displaced such that it lifts off with its first sealing surface 32 from the first valve seat 36 and a connection between the annular space 39 via the narrowing of the diameter 34 to Annulus 45 produces and so the fuel can get from the high-pressure fuel reservoir into the pressure chamber 9 via the pressure channel 12. As a result, the fuel injection valve member 2 is lifted from its valve seat 7 and fuel injection takes place. To interrupt this fuel injection or to interrupt it

Termination, the closing body 56 must get back to one of the seats 60 or 64. At that moment, the original high pressure builds up again in the working space 31 due to the inflow of high-pressure fuel via the channel 41, so that the control valve member 23 is moved back onto the first valve seat 36 and thus the inflow of high fuel pressure is prevented. This leads to the termination of the injection. In this position of the control valve member 23, the annular space 45 is connected to the space 18 via the flat 47, so that the pressure in the pressure space 9 can quickly relax. This supports a quick closing of the injection valve member.

The closing body 56 can be moved in different ways by the piezo drive. In a first mode, the piezo drive 73 can be excited and one is carried out

Movement of the closing body 56 away from the first valve seat 64 with subsequent relief of the working space 31 when it is open Relief line 50, 66 and then a restoration of the closing body 56 with its second sealing surface 61 on the second valve seat 62 and a reclosing of the relief channel. In this process, the work space 31 is relieved for a short time and then the pressure in the work space 31 is built up again to the original value. The result of this is that the control valve closing member 23 executes a short movement by also briefly establishing the connection between the pressure line 40 and the pressure channel 12, which triggers a brief injection.

Subsequently, the injection valve member 2 is immediately closed again because the connection between the pressure line 40 and the pressure channel 12 is also prevented by the reclosing of the control valve member 23. Such a short-term injection is particularly advantageous for achieving a pre-injection in diesel internal combustion engines. For a subsequent main injection, the closing body 56 is brought into a middle position between the two valve seats 64 and 60, so that the working space 31 remains relieved for a longer period of time and, accordingly, the fuel injection valve member 2 is also lifted from its valve seat for a longer time in accordance with an associated main fuel injection quantity. For an advanced pre-injection with subsequent main injection, the piezo drive 73 is thus excited so that it first moves the closing body 56 away from the second valve seat 64 to the first valve seat 60, with the result of a pre-injection. Subsequently, the closing body 56 is brought back into a middle position and is finally moved back to the second valve seat 64 in order to complete the main injection. Thus, the closing body only carries out a single back and forth movement with a corresponding one for both a pre-injection and a main injection low excitation energy for its drive at high switching speed. In particular, due to this construction, a very short injection can be controlled with the aid of a small control valve without mass movement reversal energy.

Claims

Expectations

1. Fuel injection device for internal combustion engines with a high-pressure fuel source (18), with which a pressure chamber (9) of an injection valve (1) is connected via a pressure line (40), which has an injection valve member (2) which, under the influence of the pressure chamber (9) supplied high-pressure fuel, which acts on a pressure shoulder (16) of the injection valve member against a restoring force (17), opens injection openings (8) for fuel injection and which closes to a relief channel (19) when the pressure chamber (9) is relieved and the connection of the pressure line (40) to the pressure chamber (9) and the connection of the pressure chamber (9) to the relief channel (19) are controlled by an electrically controlled, designed as a 3/2-way valve (24) with a control valve member (23) characterized in that the control valve member (23) has a piston part (28) which is displaceable in a guide bore (27) and there with its end face (2nd 9) one connected via a certain inflow cross section (42) to a pressure source of high pressure level

Working space (31) limited to reduce its pressure and to actuate the control valve member (23) by an electric Controlled pilot valve (55) is relieved via a relief line (50) and a spring-loaded valve member (54) of the pilot valve is driven by a piezo drive (73) and has a closing body (56), on the sides of which facing away from one another in the adjustment direction

Sealing surface (61, 62) are arranged, which cooperate with two valve seats (60, 64), one valve seat (60) limiting the inlet of the relief line (50) into a valve chamber (53) receiving the closing body (56) and the other the valve seats (64) limits the discharge line (50) from escaping from the valve chamber (53) and the distance between the valve seats (60, 64) is so large that in the period of time the valve element (54) of the pilot valve can be adjusted by the achievable adjustment speed the path from lifting the closing body (56) from one of the valve seats (60, 64) to putting the closing body (56) on the other of the valve seats (60, 64) is defined, a relief of the work space (31) occurs, which leads to an injection process determined by this period of time by actuation of the injection valve member (2), with the closing body (56) in an intermediate position to control a large, main injection quantity Chen two valve seats (60, 64) can be brought, in which a main injection quantity is injected over the duration of the maintenance of this intermediate position.

2. Fuel injection device according to claim 1, characterized in that the sealing surfaces (61, 62) are conical.

3. Fuel injection device according to claim 2, characterized in that the closing body (56) is arranged at one end of a plunger (57), the other end of which via a hydraulic space (71) is coupled to the piezo drive (73).

4. Fuel injection device according to claim 3, characterized in that one of the sealing surface (62) adjacent part of the plunger (57) is reduced in diameter and there together with a plunger (57) leading from the valve seat (64) outgoing guide bore ( 58) delimits an annular space (65) which is part of the relief channel (50) and from the wall of the guide bore (58) surrounding the annular space (65) a further part (66) of the relief line (50) to the relief space continues.

5. Fuel injection device according to claim 4, characterized in that in the relief line (50) preferably upstream of the valve chamber (53) a diameter limitation (51) is formed.

6. The fuel injection device according to claim 5, characterized in that the inflow cross section to the working space (31) is designed as a diameter limiter (42) in a channel (41) guided by the piston part (28) and opening on the end face (29) of the piston, which starts from an annular space (39) surrounding the control valve member (23) and connected to the pressure source (13) at a high pressure level.