EP1961953A1 - Multiway valve - Google Patents

Abstract

The control valve (10) has a valve body (12) and a controller for operating a valve element. A hub (40) is opened or closed by a valve element during multiple operation of the controller, which opens or locks another hub (64). A valve element is axially accommodated in the pressure balanced intermediate hub casing (44) in an adjustable manner. The pressure balanced intermediate hub casing is subjected to an initial tension spring (58).

Description

State of the art

EP 1 277 952 B1 refers to a fuel injector with successive, inwardly opening valves. EP 1 277 952 B1 discloses a fuel injector for fuel injection systems in internal combustion engines with a housing in which valves arranged one behind the other are accommodated. Of which one can be actuated via an actuator associated with the housing, wherein each of the valves is further associated with a aufsteuerbare chamber. The valves are designed as inwardly opening valves, wherein one of the actuatable with the actuator valves acts on the other valve via a spring assembly.

Presentation of the invention

According to the invention, a control valve is proposed which has a preferably needle-shaped valve element in the axial direction displaceable, pressure-balanced sleeve body. On a preferably needle-shaped valve element, in a first embodiment of the solution proposed according to the invention, two seats are formed, which are connected in series one behind the other and which can be designed, for example, as conical seats. With the solution shown in the first embodiment, a 4/3-way valve with two conical seats can be represented. This allows a variable switching, so for example, both seats with no-current actuator, be it a solenoid valve, be it a piezoelectric actuator, be open, be closed only one of the two seats or both seats are closed.

In this embodiment, preferably integrally formed valve element is a Zwischenhubhülse whose two end faces are subjected to preferably identical pressure. As a result, the Zwischenhubhülse is pressure balanced. The Zwischenhubhülse is acted upon by a spring element, which is located on a spring support within the solenoid valve is supported. If the actuator designed as a magnet, for example, is energized, first a first seat and then a second seat are closed, which takes place successively in successive order.

If the valve proposed according to the invention is designed as a solenoid valve, a magnetic coil is enclosed by a magnetic core. The magnetic core can be fixed on the one hand via a plate spring, which is supported on a lid which is fastened by means of a union nut on the injector body; On the other hand, it is also possible to apply a constant biasing force to the magnetic core, which encloses the magnetic coil of a solenoid valve. Both embodiments for receiving the magnetic coil or the magnetic core of the solenoid valve are possible. When the actuator is designed as a solenoid valve, a residual air gap adjustment can optionally be carried out by a "keyhole" washer and by an adjusting washer which is inserted between a stop sleeve and the "keyhole" washer.

For assembly reasons, the armature of the solenoid valve is only then attached to the needle-shaped valve element, when previously the stop sleeve mounted on this and a possibly to be provided shim has been pushed onto the preferably needle-shaped valve member. Only then does the armature be sanded or, alternatively, is the residual air gap adjusted with the help of the "keyhole" washer. This also has the function of securing the stop sleeve axially upwards.

The "keyhole" disc can also be omitted and replaced by a normal perforated disc. If a normal perforated disc is used, designed as a pressure balanced Zwischenhubhülse stop sleeve is formed two or more parts to ensure mounting capability. The valve element of the inventively proposed valve is designed so that the seat diameter in the region of the first, for example designed as a conical seat corresponds to the guide diameter of the preferably needle-shaped injection valve member in the injector body or a needle seat sleeve, and the seat diameter of the second seat of the preferably needle-shaped valve element a further guide diameter of the needle-shaped valve element corresponds. As a result, the needle-shaped valve element is pressure balanced.

It is possible, both the second seat, which may be formed, for example, as a conical seat, either in the valve body or the second seat also on a preferably needle-shaped valve member surrounding needle seat sleeve, be it one or more parts designed to execute. Both embodiments are possible. Instead of in In a first embodiment designed as a conical seats these seats can also be designed as a slide or flat seats.

In a further advantageous embodiment of the proposed solution according to the invention, the valve comprises two preferably needle-shaped valve elements, which are controllable similar to the embodiment described above. The two preferably needle-shaped valve elements are received lying one behind the other. The two used in the second embodiment of the invention proposed solution, preferably needle-shaped valve elements are characterized by their shorter length. A shorter overall length means that in a finish, such as a high-precision machining operation such as grinding, which is essential in the manufacture of valves, a lower deflection occurs and that thus a better tolerance can be achieved. The arrangement shown in the second embodiment of the proposed solution according to the invention also comprises the stop sleeve accommodated on a valve needle and slidably received on the circumference of the needle-shaped valve element. The stop sleeve is supported by means of a spring element, which is supported either on the injector body or on a needle seat sleeve.

The two preferably needle-shaped, shorter valve elements are preferably exposed at a contact point to a return pressure level, so that the facing end faces are depressurized. Between two valve elements game is formed. While an upper seat is designed as a conical seat on one of the two preferred needle-shaped valve elements according to the second embodiment of the invention underlying idea, in the seating area of the other, also needle-shaped valve element, a first lower and a second lower seat are executed. With the second embodiment of the invention, a control valve can be provided which contains an actuator - here as a solenoid valve - and two separate, preferably needle-shaped valve elements having a multi-way switching function for controlling at least two different functions or control spaces allows. For example, a UI filling and / or a stepped needle control can take place.

In a further, third embodiment of the invention underlying idea, a control valve is proposed, which also includes a controller, which may be formed, for example, as a magnetic actuator, and two separate, preferably needle-shaped valve elements. The two preferred needle-shaped valve elements also build shorter - with respect to the first embodiment, similar to second embodiment - so that in finishing operations, such as grinding operations, a lower deflection occurs, which affects the tolerances more favorable. Even with the third embodiment of the invention underlying idea can be a multi-way switching function for controlling at least two different functions, such as a needle control and secondly the control of a pressure booster realize. Since, according to these embodiments, after a first stroke, the first seat is open, this can for example be used to control a nozzle-shaped injection valve member. The first lower seat and the second lower seat, however, can be used to control a pressure booster. After passing through a first stroke, the first lower seat is still in a closed position. Position 70 is connected to high pressure port 114, while position 62 is connected to a return port. Thus, the drive chamber of the booster, ie the differential pressure chamber of high pressure is applied, and the pressure booster thus not active. After passing through the second further stroke, the first lower seat is opened and the second lower seat is closed. Thus, the control room, ie the differential pressure chamber of the booster, connected to the return and thus separated from the high pressure or the system pressure. Thus, the pressure booster is activated and it enters the desired according to the transmission ratio of the booster pressure increase.

In the third embodiment of the invention underlying idea, the stop sleeve according to the two embodiments described above is omitted and replaced by a spacer sleeve. The spacer sleeve supports a stop sleeve within the valve body of the control valve proposed according to the invention. While the first, preferably needle-shaped valve element, a first seat is designed as a conical seat, are located on another, also preferably needle-shaped valve element, an upper and a lower seat, the stop surfaces are formed either by needle seat sleeves or a needle seat sleeve and a control edge on the Valve body of the control valve is executed. The first seat, which is arranged on the first, preferably needle-shaped valve element, is turned over in comparison with the two embodiments described above. The spacer sleeve encloses a closing spring, which adjusts the first, preferably needle-shaped valve element in the seat against a stop on the stop sleeve.

In the third embodiment of the invention underlying the idea needle seat sleeves can be used, for example, enclose the further, preferably needle-shaped valve member and enclose a portion of the first, also preferably needle-shaped valve element. The at least one needle seat sleeve can be formed in one or more parts and have a first and a second needle seat sleeve portion. The at least one needle seat sleeve is trapped within a spring holder. The at least one needle seat sleeve is acted upon by a spring supported in the valve body. In the valve body there is also a further spring element, which acts exclusively on the further valve element guided in the at least one needle seat sleeve or in a first needle seat sleeve section. Also in the third embodiment, the two mutually facing end faces of the preferably needle-shaped valve elements are relieved of pressure, as they are in the region of a return to the low pressure region of the control valve proposed according to the invention.

Brief description of the drawings

With reference to the drawing, the invention will be described below in more detail.

Figur 1

eine erste Ausführungsform des erfindungsgemäß vorgeschlagenen Steuerventils mit einer am Umfang des nadelförmig ausgebildeten Ventilelementes aufgenommenen, in axiale Richtung verschiebbaren Zwischenhubhülse,

Figur 1.1

das hydraulische Schaltschema der in Figur 1 dargestellten Ausführungsform,

Figur 1.2

Kraft-/Weg-Verläufe der Federelemente der in Figur 1 dargestellten Ausführungsform,

Figur 2

eine weitere Ausführungsform der erfindungsgemäß vorgeschlagenen Lösung mit zwei separaten, nadelförmig ausgebildeten Ventilelementen,

Figur 2.1

Kennlinien der in der Ausführungsform gemäß Figur 2 gesetzten Federelemente,

Figur 3

eine weitere, dritte Ausführungsform des erfindungsgemäß vorgeschlagenen Steuerventils mit zwei separaten, nadelförmig ausgebildeten Ventilelementen ohne Zwischenhubhülse und

Figur 3.1

die Kennlinienverläufe der Federelemente der in Figur 3 dargestellten Ausführungsform.

Show it

FIG. 1

a first embodiment of the present invention proposed control valve with a received on the circumference of the needle-shaped valve member, axially displaceable Zwischenhubhülse,

Figure 1.1

the hydraulic circuit diagram of in FIG. 1 illustrated embodiment,

Figure 1.2

Force / displacement curves of the spring elements of in FIG. 1 illustrated embodiment,

FIG. 2

a further embodiment of the proposed solution according to the invention with two separate, needle-shaped valve elements,

Figure 2.1

Characteristics of the embodiment according to FIG. 2 set spring elements,

FIG. 3

a further, third embodiment of the invention proposed control valve with two separate needle-shaped valve elements without Zwischenhubhülse and

Figure 3.1

the characteristic curves of the spring elements of in FIG. 3 illustrated embodiment.

embodiments

The control valve described below in various embodiments may be used in common rail or in pump / nozzle (UI) applications or other injection systems, as well as in control and circuit technology. The control valve is suitable for use on self-igniting internal combustion engines and spark-ignited internal combustion engines, whether they are mixed-processing, be it direct-injection, spark-ignited internal combustion engines.

The representation according to FIG. 1 shows a first embodiment of the invention proposed control valve, which has a single, preferably needle-shaped valve element, on the circumference of a pressure balanced Zwischenhubhülse is received, which is axially displaceable and is preferably biased with eienr spring.

From the illustration according to FIG. 1 shows that a control valve 10 has a valve body 12 in which a valve element, which is preferably designed as a valve needle 38, displaceable in the vertical direction, is added.

This in FIG. 1 illustrated control valve 10 includes a magnetic coil 16 which is received within a magnetic core 28. On formed as a valve needle 38 valve element, a disc-shaped anchor is attached to a joint 14, which cooperates with the magnetic core 28 enclosed by the magnetic coil 16. The magnetic core 28 can be applied by means of a constant biasing force 30 applied to the magnetic coil 16 on or to a this partially enclosing intermediate disc; Alternatively, it is also possible to employ the magnetic core 28 by means of at least one plate spring 26 with the interposition of at least one seal 18 resiliently to the magnetic core 16. The at least one plate spring 26 is in the in FIG. 1 illustrated embodiment, the lid 20 is acted upon, which is connected by means of a union nut 22 with the valve body 12 of the control valve 10.

If a magnetic coil 16 is used as a controller of the control valve 10, then a residual air gap of the magnetic actuator and its stroke can be set with a "keyhole" washer 24 and a stroke adjusting disk 32 associated therewith.

Preferably, the valve element is designed as a valve needle 38, on which a stop sleeve 34 is received. The stop sleeve 34 is accommodated on the valve element designed as a valve needle 38 in a region in which this formed in a first diameter d ₁ is. The stop sleeve 34 is mounted before the joining of the armature disk at the joint 14 with the valve element designed as a valve 38 and may optionally take on a bias function. Alternatively, the stop sleeve 34 may also be omitted if a diameter d _{2 of} the needle-shaped valve element is dimensioned according to the outer diameter of the aborted stop sleeve. This allows the valve needle lead and also separate the pressure above the first seat of a magnetic space. This also offers the possibility to mount or press the anchor at any time. For this purpose, the starting position of Zwischenhubhülse 44, which was previously defined by the stop sleeve 34, for example, determined with a retaining ring which is inserted above the Zwischenhubhülse 44, for example, in a rectangular groove in the valve body 12 and thus also realized the spring bias of the spring 58.

With respect to the stop sleeve 34, the needle-shaped valve element 38 is movable within a first stroke 56. Below a collar on the valve needle 38, an upper seat 40 is formed, which in the in FIG. 1 illustrated embodiment of the control valve 10 is designed as a conical seat. Below the upper seat 40 extends to the valve needle 38 has a conical surface 42. The collar is formed in a diameter d ₂ on the valve needle 38, the diameter at the upper seat 40 of the valve needle 38 denoted by d ₃ . Below the seat diameter d _{3 of} the valve needle 38, this assumes a reduced diameter d ₄ .

In the region in which the preferably needle-shaped valve element 38 has the diameter d ₄ , the Zwischenhubhülse 44 is taken substantially. This has a breakthrough, so that the area below the upper seat 40 with the seat open 40 with the opening of the intermediate sleeve 44 in the valve body 12 opening second bore 48 is connectable. The first bore 46 in the valve body 12 communicates via a connection 50 with a third bore 60 in the valve body 12 in connection, which opens below the Zwischenhubhülse 44 into a cavity in the valve body 12 , Since the first bore 46 and the third bore 60 are hydraulically connected to each other via the connecting line 50, the first end face 52 and the second end face 54 of the Zwischenhubhülse 44 are pressure balanced. By possibly introduced throttle points and pressure differences could be exploited.

The Zwischenhubhülse 44 is optionally supported with the interposition of a disc on a biasing spring 58, which in turn is supported either in the valve body 12 or on an upper end side of a needle seat sleeve 72. From the illustration according to FIG. 1 going show that both Abstützvarianten the biasing spring 58 are possible. On the one hand, in the right part of the FIG. 1 shown that the biasing spring 58 is supported on the needle seat sleeve 72, while in the left part of the FIG. 1 is shown that the biasing sleeve 58 is supported directly on a recess in the valve body 12 of the control valve 10.

The second seat 64 is also formed as a conical seat, indicated by a conical surface 66 on the circumference of the preferably needle-shaped valve element 38 of the control valve 10. Depending on the embodiment, ie whether guided in the valve body 12 valve element 38th or in the needle seat sleeve 72 guided valve member 38, the second seat 64 is carried out either in the valve body 12 or on a control edge of the needle seat sleeve 72. Above the second seat 64, the fourth bore 62 opens; below the second seat 64 opens a fifth bore 70. The fourth bore 62 and the fifth bore 70 are - in the embodiment with needle seat sleeve 72 - provided in the wall openings provided with valve chambers above and below the second seat 64. A seat diameter of the second seat 64 is denoted by d ₅ . This is identical to a diameter d _{7 of} the needle-shaped valve element 38, so that it is pressure-balanced in the region below the second seat 64. If the aforementioned second seat 64 is defined by the diameter d _{3 of} the preferably needle-shaped valve element 38 and the lower conical surface, it follows that the area above the second seat 64 is pressure-balanced. At the fourth bore 62 and the fifth bore 70 according to the in FIG. 1 In the illustrated embodiment, for example, the nozzle part of a pump-nozzle system may be connected.

Below the seat diameter d ₅ , the preferably needle-shaped valve element 38 has a reduced diameter d ₆ . For the sake of completeness it should be mentioned that a diameter d _{3 of} the needle-shaped valve element 38 in the region of Zwischenhubhülse 44 corresponds to the seat diameter d _{3 of} the first seat 40, so that the needle-shaped valve element 38 is also pressure balanced in the region of the first seat 40.

Eventually, the diameter of the first seat 40 can be selected so that it exceeds the diameter d ₃ , so that a pressure stage is formed. The spring element 76 can be omitted in this case. In this embodiment, the stop sleeve 34 may also be omitted, so that the high pressure or the system pressure with closed first seat 40 is present within the pressure balanced Zwischenhubhülse 44. The resulting due to the difference in diameter pressure stage acts in the opening direction.

Below the needle seat sleeve 72 is a return spring 76, which acts on the lower end face of the needle-shaped valve element 38. Below the return spring 76 in the spring holder 77 is a low-pressure side return 74 runs. At the first bore 46, which is in communication with the third bore 60, for example, the inlet for a pump-nozzle system can be connected by closing the first seat 40 is operable, or be connected to a delivery pump for the promotion of fuel. At the second bore 48, a piston chamber 198 is connected (see also FIG. 6 ). At the fourth bore 62, for example, a control chamber pressure of the injection nozzle may be present, while at the fifth bore 70, a low-pressure side return can be connected.

The operation of the first embodiment of the present invention proposed control valve 10 according to FIG. 1 Is as follows:

When energizing the solenoid 16, the armature of the solenoid valve is tightened and in accordance with the first embodiment FIG. 1 integrally formed needle-shaped valve element 38 moves in the vertical direction downwards. In this case, first the first seat 40 is closed, ie, the conical surface 42 is in the first end face 52 of the pressure-balanced Zwischenhubhülse 44. Thus, the first seat 40 is closed. Due to the connection 50 of the first bore 46 with the third bore 60, the Zwischenhubhülse 44 is pressure-balanced at its first end face 52 and its second end face 54. With continued energization of the solenoid 16 of the armature continues in the vertical direction down, so that the Zwischenhubhülse 44 is pressed by the acting on the first end face 52 needle-shaped valve element 38 in the vertical direction downward against the action of the biasing spring 58. As a result, the second seat 64 is closed. The needle-shaped valve member 38 first moves into the first seat 40. Since the intermediate stroke sleeve 44 is biased by the biasing spring 58, there is a force jump that must overcome magnetic force to bring the needle-shaped valve member 38 into the second seat 64 and therein to be able to hold.

After closing the second seat 64, ie when both seats 40, 64 are closed, the force applied by the solenoid 16 is balanced with the restoring force of the biasing spring 58, the return spring 76 and the resulting seat force in the second seat 64. By the in FIG. 1 As shown in the first embodiment of the control valve 10, the first seat 40 and the second seat 64 may be closed, both seats 40, 64 may be open, and the first seat 40 may be closed while the second seat 64 is open as shown in FIG in Figure 1.1 indicated switching diagram.

The first bore 46 communicates with the third bore 60 via the connection 50 and may be connected to the second bore 48 either by opening or closing the first seat 40, while the fourth bore 62 or the fifth bore 70 is in the lower region of the first bore 40 Valve body 12 of the control valve 10 can be connected together or separated from each other. Thus, the switching valve 10 with the Zwischenhubhülse 44 three switching positions at four ports and acts as a 4/3-way valve.

The representation according to Figure 1.1 is the hydraulic circuit diagram of in FIG. 1 shown first embodiment of the present invention proposed control valve.

From the illustration according to Figure 1.1 it follows that the control valve 10 by the actuator, which in the embodiment according to FIG. 1 is designed as a magnetic coil, can be placed in 3 different positions. In the illustration according to Figure 1.1 is the needle-shaped valve element 38 acted upon by the return spring 76, indicated. In a first switching position 78, the first seat 40 and the second seat 64 are open, so that the first bore 46, which is connected to the third bore 60, are hydraulically connected to the second bore 48. In a second switching position 80, the first seat 40 is closed and the second seat 64 open, so that the fourth bore 62 is in communication with the fifth bore 70. In the in Figure 1.1 Finally, third switching position 82 shown schematically, both the first seat 40 and the second seat 64 are closed. From the circuit diagram as shown in Figure 1.1 shows that the embodiment of the invention proposed control valve 10 as shown in FIG FIG. 1 represents a 4/3-way valve having two seats 40, 64, which in the embodiment according to FIG. 1 are designed as conical seats.

Figure 1.2 shows the characteristics of the spring elements of in FIG. 1 illustrated embodiment.

From the characteristic curves as shown in Figure 1.2 , referring to the embodiment of the control valve 10 according to FIG. 1 refer, it is apparent that in A the needle-shaped valve element 38 abuts in a first switching position on the stop sleeve 34. When the solenoid valve 16 is actuated, the first seat 40 closes at B. This corresponds to a second switching position. If the solenoid valve 16 continues to be energized, the closing of the second seat 64, which is completely closed at D, begins when C is reached. In this position, the control valve 10 has its in Figure 1.1 82 is reached by the first seat 40 at B and the second seat 64 at D according to FIG the representation in Figure 1.2 are closed, which the third shift position 82 according to Figure 1.1 equivalent. The index .2 indicates the point at which an increase in the contact force in the seat can be achieved by further increasing the magnetic force by energizing the magnetic coil 16.

FIG. 2 shows a further second embodiment of the invention proposed control valve with two separate, preferably needle-shaped valve elements.

In the FIG. 2 illustrated second embodiment of the control valve 10 includes the valve body 12, in which the first valve element 38 and another valve element 108 are integrated. In the upper region of the valve body 12 of the actuator - here designed as a magnetic coil 16 - embedded in the magnetic core 28 is arranged. The magnetic core 28 and the magnetic coil 16 can - as in FIG. 2 shown - be acted upon either by a constant biasing force 30 or alternatively be biased by means of the lid 20 which is fixed by the union nut 22 on the valve body 12. For sealing between the cover 20 and the valve body 12 at least one annular seal 18 is provided. In the in FIG. 2 illustrated embodiment is located below the attached to the joint 14 with the valve member 38 anchor a return spring. This can be both - as in FIG. 2 shown - on the Hubeinstellscheibe 32 and the stop sleeve 34, as well as on a spring support 100 of the "keyhole" disc 24 support.

Analogous to in FIG. 1 the first embodiment shown is located within the valve body 12, the stop sleeve 34. Between this and a collar on the circumference of the valve element 38, a first stroke 56 is formed. At the level of the collar, the stop sleeve 34 has at least one opening 36, which is formed in the valve body 12, the first bore 46 opposite. The first bore 46 is hydraulically connected via the connection 50 with the third bore 60.

Below the collar, the valve element 38 has the conical surface 42, through which, in interaction with the Zwischenhubhülse 44, the first seat 40 is formed. Since the first bore 46 above the first seat 40 via the connection 50 with the third bore 60 is hydraulically in communication, the first end face 52 and the second end face 54 of Zwischenhubhülse 44 are subjected to identical pressure levels, so that it is pressure balanced.

The Zwischenhubhülse 44 is disposed on the circumference of the needle-shaped valve element 38, wherein the seat diameter of the first seat 40 corresponds to the guide diameter of Zwischenhubhülse 44 on the circumference of the needle-shaped valve element 38. The Zwischenhubhülse 44 is acted upon by the biasing spring 58 at the second end face 54 with the interposition of an insert disc. Analogous to the representation according to FIG. 1 the biasing spring 58 may be supported either directly on the valve body 12 or on the end face of a one-piece needle seat sleeve 72 or on a multi-part needle seat sleeve 110, 112.

Below the needle-shaped valve element 38, the further valve element 108 is mounted in the valve body 12 or the multipart guide sleeve 110, 112. Its upper end face lies at a distance 128 from the end face of the needle-shaped valve element 38. In the region of this distance 128, a return line 102 opens into the valve body 12 or the first guide sleeve part 110. The two facing end faces of the valve element 38 and of the further valve element 108 are thereby in the range of 128 distance, which represents a game relieves pressure. On the further valve element 108, a first lower seat 104 and a second lower seat 106 are formed. These can be designed, for example, as conical seats and as a slide. Via the further valve element 108, the bores opening out below the return 102, ie the fourth bore 62, the fifth bore 70 and the sixth bore 114 can be controlled for versatile applications. The further valve element 108 constitutes a 3/3-way control valve. Summarized with the valve element 38, the control valve 10, as shown in FIG FIG. 2 a 5/4-control valve, which replaces two valves with a separate actuator or separate magnet through a valve with a controller. Missing the sixth bore 114, the disc 132 and the first return spring 116, and eliminating the intermediate stroke 130 is, by the control valve 10 as shown in the embodiment in FIG. 2 given a 4/3 valve which replaces two valves with one.

Another advantage with the in FIG. 2 embodiment is achievable, is that due to the shorter length of the valve elements 38 and 108, the deflection in the finishing grinding is much lower. As a result, the shorter valve element 38 and the further valve element 108 can be produced in a higher processing quality, since these are less spherical, which is attributable to their lower deflection.

The first lower seat 104 formed on the further valve element 108 cooperates with a seat surface, which is formed either below a first opening 120 of the second guide sleeve section 112, or which can be formed directly on the valve body 12. By contrast, the second lower seat 106 on the further valve element 108 cooperates with a second control edge 126 of the first guide sleeve section 110. Below the second seat 106 extends on the further valve element 108 a first control edge 124. The first guide sleeve portion 110 is supported by a ring 132. The ring 132 in turn is acted upon by a first return spring 116, which encloses a further, second return spring 118, which acts on the further valve element 108. The first return spring 116 acts on the first guide sleeve section 110, the first guide sleeve section 110 representing the stop for the first return spring 116. About a shim whose preload is determined. The first guide sleeve portion 110 is supported by the spring holder 77 and fixed in the axial direction. The functioning of in FIG. 2 illustrated embodiment of the control valve 10 is as follows:

When current is applied to the solenoid 16 of the actuator designed as a magnet, the armature connected at the joint 14 with the needle-shaped valve element 38 is attracted. As a result, the armature moves counter to the spring effect of the biasing spring, which is supported on the stop sleeve 34 and the spring seat 100 of the "keyhole" washer 24 in the vertical direction downwards and provides the collar on the circumference of the valve element 38 in the first seat 40th By the further energization of the solenoid 16, the intermediate sleeve 44, which is supported on the biasing spring 58, pressed down until after overcoming the game 128, the lower end face of the valve element 38, the further valve element 108 contacted. Since this is biased by the second return spring 118, this is placed in the idle state before contacting by the valve element 38 in the first lower seat 104, which is therefore closed.

If, after overcoming the distance 128, the further valve element 108 is acted upon by the lower end face of the valve element 38, the first lower seat 104 is opened counter to the action of the first return spring 118. If the first return spring 118 is preloaded, a force jump takes place at E in the diagram. The magnetic force to be applied by the solenoid valve 16 must overcome this force jump, so that the seat 104 opens.

After opening seat 104, the further valve element 108 passes through the cavity formed within first guide sleeve portion 110 until the distance represented by intermediate stroke 130 is used up. There force jump 116. 124 is still in overlap with 126, only at a further increase in the magnetic force moves the needle 108 to stop (stroke stop in FIG. 2 added). Slide edge 124 is just below 126, resulting in connection of 114 with other holes (alternatively, stroke 108 could hit 110 on the lower cone, but then 106 or the lower cone would need to have bevels to make connection).

By the in FIG. 2 illustrated second embodiment of the control valve 10 can be connected by the first seat 40, the first bore 46 and the third bore 60 with the second bore 48. Depending on the position of the further valve element 108, the fourth bore 62 and the fifth bore 70 can be separated or connected to one another by the first lower seat 104. In addition, in the end position, the fourth bore 62 is connected to the fifth bore 70 and the sixth bore 114.

Figure 2.1 shows a schematic representation of the characteristics of the embodiment in accordance with FIG. 2 used spring elements.

From the illustration according to Figure 2.1 shows that at A, the valve element 38 at the stop, ie the lower end face of the stop sleeve 34, is applied. After reaching point B, the valve element 38 has moved into the first seat 40, this is therefore closed. The energization of the solenoid 16 causes the Zwischenhubhülse 44 is moved against the action of the biasing spring 58 by the closed first seat 40 and the valve element 38 down, but only after exceeding the preloaded spring. At E, the game 128 is used up, ie the distance 128 pass through, the first lower seat 104 opens only after exceeding the spring force applied by the prestressed spring. The same applies to the operating state G. After reaching the state G, the intermediate stroke 130 is used up, the valve element 108 is in the middle position, while reaching point I, the second lower seat 106 strikes by abutment against the second control edge 126. Alternatively, the valve element 38, 108 moves in point I to a stroke stop shown sketchy. In this latter position I are the magnetic force with the spring force of the biasing spring, the biasing spring 58 and the first and second return spring 116 and 118 in equilibrium, therefore with all the spring forces and the contact force at the stop. Reference symbol J indicates a further increase in the magnetic force, whereby the contact force is increased again.

FIG. 3 shows a further embodiment of the invention proposed control valve with two separate valve elements, but without Zwischenhubhülse.

Unlike in FIG. 2 illustrated embodiment is in the in FIG. 3 illustrated embodiment of the present invention proposed control valve Zwischenhubhülse 44 omitted. This is replaced by a spacer sleeve 150, which in the valve body 12, the stop sleeve 34 is supported.

Unlike in FIG. 3 illustrated embodiment of the invention proposed control valve 10 with two separate valve elements 38, 108 is the federal government, to the conical surface 42, which forms the first seat 40, formed on the circumference of the valve element 38 in the reverse direction. The spacer sleeve 150 encloses the biasing spring 58, which in contrast to in FIG. 2 illustrated embodiment of the control valve 10 is no longer integrated in the solenoid part, but in the injector body 12, and the collar, ie the first seat 40, acted upon in the closed position.

Above the first seat 40, the second bore 48 opens. The second bore 48 either represents the high-pressure connection or can also be used as Absteuerbohrung for the control of tax amount to be actuated injection valve member. The high-pressure connection can also be connected to the third bore 60. With respect to the second bore 48 and the third bore 60, the respective other bore may represent the low-pressure side connection to the return, if at one of the two holes 48 and 60, the high-pressure connection is realized.

Below the first seat 40 opens in the injector valve body 12, the third bore 60, which may be connected, for example, with the return, while the second bore 48 may be connected, for example, with the flow of a control chamber of a fuel injector and the control amount absteuert.

Between the valve element 38 and the further valve element 108 is a disc. In contrast to the representation according to FIG. 2 , in the game between the lower end face of the needle-shaped valve element 38 and the upper end face of the valve element 108 prevails, this is in the in FIG. 3 shown used second switching position. This in FIG. 2 shown game is because the needle-shaped valve member 38 can still drive together with the sleeve on the second, further valve element 108 (see Kraftwegdiagramm from B to E). This path is in the in FIG. 3 Switch position shown omitted, since there is no sliding sleeve. From the illustration according to FIG. 3 shows that the first lower seat 104 is closed and the fourth hole 62 separates from the fifth hole 70. The further valve element 108 is analogous to the embodiment according to FIG FIG. 2 trained guide sleeve sections 110, 112 with their respective openings 120, 122 enclosed. Alternatively, the further valve element 108 may also be guided directly in the valve body 12.

In the operating position according to FIG. 3 the second lower seat 106 is opened so that the fifth bore 70 is hydraulically in communication with the sixth bore 114. In this case, the first control edge 124 and the control edge 126 in the first guide sleeve portion 110 are ineffective.

By the formation of the intermediate stroke 130, the further valve element 108 is acted upon only by the second return spring 118. The first return spring 116 is supported on the first guide sleeve portion 110, which represents the stop for the first return spring 116. The shim 132 serves to adjust the spring bias applied via the first return spring 116 and as a driver for the further valve element 108 so as to define the intermediate stroke 130. The first guide sleeve portion 110 is supported from below by the spring holder 77. The intermediate stroke 130 enables a three-way function of the further valve element 108.

While at the second bore 48, for example, the flow of a control chamber of a fuel injector may be connected to the third bore 60, for example, the low-pressure side return of the fuel injector can be connected. Reference numeral 102 marks a low-pressure side return over which the two opposite end faces of the valve element 38 and the further valve element 108 are pressure-relieved. At the fourth bore 62, for example, a return port can be connected, while at the fifth bore 70, the control bore for a pressure booster of a fuel injector can be connected and at 114, d. H. the sixth hole, an inlet of the pressure booster can be connected.

With the in FIG. 3 illustrated embodiment of the control valve 10 can be controlled via the further valve element 108, a pressure booster. Via the intermediate stroke 130 and the second return spring 118, the further valve element 108 is given a three-way function; if the intermediate stroke 130 is not formed, the second return spring 118 and the disc 132 is missing, the control valve 10 is a total of a 5/3-way valve. Disclaims the sixth bore 114, the intermediate stroke 130, the ring 132 and the second return spring 118, represents the control valve 10 as a whole, a 4/3-way valve. If the control valve 10 is formed as shown in the illustration FIG. 3 , so this represents a 5/4-way control valve for use in a fuel injector. With the in FIG. 3 embodiment illustrated can be achieved in the realization of the intermediate stroke 130, the provision of the ring 132 and the second return spring 118 both a pressure booster connection and the control of a nozzle of a fuel injector.

With a steller, in the representation according to FIG. 4 a solenoid 16, the control valve 10 can be actuated. By the in FIG. 4 illustrated "upturned" first seat 40, which is designed as a conical seat 42, an opening of the first seat 40 upon actuation of the solenoid 16 is achieved against the action of the biasing spring 58. As the valve element 38 continues to move downwards, it strikes the further valve element 108, which is biased by the first return spring 118. In the embodiment according to FIG. 4 opens in the end position of the first lower seat 104, while the second lower seat 106 closes. This is advantageous for controlling a pressure booster.

The representation according to Figure 3.1 are the characteristic curves of the spring elements of in FIG. 3 illustrated embodiment of the control valve 10 proposed according to the invention can be seen in detail.

From the illustration according to Figure 3.1 shows that at A, the valve element 38 is placed by the action of the biasing spring 58 in the first seat 40. Upon reaching the point K, a contact of the valve element 38 with the other valve element 108 is formed. This contact is also present with increasing magnetic force at "L". Upon reaching the point A, the first seat 40 is closed. In K, the valve member 38 strikes the valve element 108. At L, the magnetic force is further increased by the solenoid 16 so that the valve element moves only when the biasing force of the second return spring 118 is overcome. Upon reaching the point M, the valve elements 38, 108 move until the intermediate stroke 130 is used up and is zero. In N, the magnetic force is further increased by the solenoid 16 until the biasing force of the first return spring 116 is reached. At O, the further valve element 108 moves into the second lower seat 106. According to P, the magnetic force can be further increased by further energization of the solenoid 16, so that the closing force achieved in the seat can be increased again.

In the illustration according to FIG. 4 the control valve proposed by the invention is shown with connections to a pressure booster and / or to an injection valve with such a fuel injector.

FIG. 4 can be taken that a pressure booster 160 is supplied via a high-pressure pumping unit 162 with fuel under system pressure. The pressure intensifier 160 includes a pressure booster piston 164 having a first major diameter 172 and a second minor diameter 174. The ratio of the squares of the diameters 172 and 174 of the pressure intensifier piston 164 defines its gear ratio. The pressure intensifier 160 comprises a differential pressure chamber 166 and a compression chamber 168. To refill the compression chamber 168, a check valve 170 is received in the pressure booster piston 164. With reference numeral 176 is a drain of a control room, designated by reference numeral 178 of the inlet to the control room. By pressure relief or pressurization of the control chamber via the outlet 176 and the inlet 178 is a preferably needle-shaped injection valve 180th actuated. This is slidably received in a vertical direction in a nozzle body 182 of a fuel injector. The control chamber of this fuel injector is designated by reference numeral 184 and contains a closing spring 186. In the inlet 176 and in the outlet 178 there is in each case a throttle 188th

This in FIG. 4 schematically dargstellte inventively proposed control valve 10 is acted upon by the magnetic coil 16 and acts against at least one spring as shown schematically in FIG FIG. 4 indicated. The third bore 60 and the fourth bore 62 are connected to a return to a fuel reservoir at the fifth bore 70, the differential pressure chamber 166 of the booster 160 is connected. At the right-hand bore 114, the high-pressure inlet via the fluid compressed in the high-pressure delivery unit 162 is in the present case fuel. About the second bore 48 of the control chamber 184 of the fuel injector is depressurized.

In the illustration according to FIG. 5 a control valve proposed according to the invention is shown schematically as in FIG. 3 reproduced on average.

The representation in FIG. 6 is a schematic representation of a pump / nozzle injection system to take.

The representation according to FIG. 6 can be taken that a serving as a high pressure source pump / nozzle system 190 and the present invention proposed control valve 10 actuated by the solenoid 16, a fuel injector can be acted upon with fuel. The pump / nozzle system 190, which is shown here as an alternative to a high-pressure delivery unit, comprises a cam 192 which acts on a piston 194. The piston 194 is guided in a pump body 196. In the pump body 196 there is a piston chamber 198. This piston chamber 198 is connected on the one hand to an annular space surrounding the injection valve member 180 which carries high pressure, and on the other hand to the inlet of the fuel tank. The latter connection can be interrupted or connected via the switching function of the upper seat 46, 60, 48, so that the pump sees high pressure or not. Via the control valve 10 and its bores 62, 70, cf. FIGS. 1 and 1.1 , the control chamber 184 via the outlet 176 and the inlet 178 can be depressurized or pressurized, so that the needle-shaped injection valve member 180 releases either formed at the combustion chamber end end injection openings or closes them. For the sake of completeness it should be mentioned that an outlet throttle 202 is formed in the outlet 176 of the control chamber 184, while in the inlet to the control chamber 184 of the FIG. 6 schematically indicated fuel injector is an inlet throttle.

Claims (12)

Control valve (10), in particular for actuating fuel injectors of internal combustion engines with a valve body (12) and an actuator (16, 28), for actuating at least one valve element (38, 108), characterized in that in the case of multiple actuation of the actuator (16, 28 ) a first seat (40) is opened or closed by the at least one valve element (38, 108) which opens or closes a further second seat (64; 104, 106). Control valve according to claim 1, characterized in that on the at least one valve element (38, 108) a pressure-balanced Zwischenhubhülse (44) is received axially displaceable. Control valve according to claim 2, characterized in that the pressure-balanced Zwischenhubhülse (44) by a biasing spring (58) is acted upon, which is supported on the valve body (12) or on a one- or multi-part guide sleeve (72, 110, 112). Control valve according to claim 1, characterized in that the first seat (40) and the at least one further seat (64; 104, 106) are designed as a conical seat. Control valve according to claim 1, characterized in that the control valve (10) comprises a one-piece valve element (38), on which a first seat (40) and a further second seat (64) are formed and the valve element (38) by a return spring ( 76) is acted upon,
or
in that the control valve (10) has a first and a further valve element (38, 108), wherein at least one seat (104, 106) is formed on the first valve element (38) of the first seat (40) and on the further valve element (108). Control valve according to claim 5, characterized in that when prestressed biasing spring (58) and biased first return spring (116), the first valve element (38) contacts the second further valve element (108) and a further stroke of the contacting valve elements (38, 108) an intermediate stroke (130) is defined. Control valve according to Claim 5, characterized in that the end faces of the first valve element (38) and of the further valve element (108) lie opposite one another in the region of a return port (102) on the valve body (12), forming a spacing (128). Control valve according to claim 5, characterized in that the actuation of the further valve element (108) by the valve element (38) which is actuated by the actuator (16, 28) takes place, and the further valve element (108) controls a pressure booster, the connected to terminals (62, 70, 114). Control valve according to claim 5, characterized in that the valve element (38) and the further valve element (108) constitute a 5/3-way valve. Control valve according to claim 1, characterized in that the first valve element (38) in the region of the first seat (40) and the further second seat (64), each seat diameter (d ₃ , d ₅ ), having the guide diameter (d ₃ , d ₇ ) of the valve element (38). Control valve according to claim 5, characterized in that the further second seat (64) is designed as a slide seat. Control valve according to claim 5, characterized in that on the further, second valve element (108) preferably two seats (104, 106) are formed, which are formed as mutually oppositely oriented conical seats.

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