Patent Abstract:
A fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, having a pressure booster in which the piston divides a work chamber, acted upon permanently by fuel via a pressure source, from a pressure-relievable differential pressure chamber. A pressure change in the differential pressure chamber is effected via an actuation of a servo valve. The control chamber of the servo valve can be pressure-relieved via a relief valve and which opens or closes a hydraulic connection of the differential pressure chamber with a return. For closing the servo valve piston, the control chamber can be acted upon by a fuel volume diverted from the differential pressure chamber. The action of fuel on the control chamber is effected via lines that contain throttle restrictions. A pressure relief of the control chamber is effected via a relief valve into a return on the low-pressure side.

Full Description:
BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   This invention is directed to an improved fuel injector, having a pressure booster, for injecting fuel into an internal combustion engine. 
   2. Description of the Prior Art 
   Stroke-controlled fuel injection systems with a high-pressure collection chamber (common rail) are increasingly used for introducing fuel into the combustion chambers of direct-injection internal combustion engines. The advantage of this is that the injection pressure of the fuel into the combustion chambers can be adapted to the engine load and engine speed. For reducing emissions and to attain high specific power levels, a high injection pressure is required. Since the attainable pressure level in high-pressure fuel pumps is limited for reasons of strength, to further increase the pressure in fuel injection systems with a high-pressure collection chamber (common rail), a pressure booster can be used in the fuel injector. 
   German Patent Disclosure DE 101 23 913 relates to a fuel injection system for internal combustion engines that has a fuel injector which can be supplied from a high-pressure fuel source. A pressure booster device that has a movable pressure booster piston is connected between the fuel injector and the high-pressure source. The pressure booster piston divides a chamber, which can be connected to the high-pressure source, from a high-pressure chamber that can be made to communicate with the fuel injector. By filling a return chamber of the pressure booster with fuel, or evacuating fuel from the return chamber, the fuel pressure in the high-pressure chamber can be varied. The fuel injector has a movable closing piston for opening and closing injection openings. The closing piston protrudes into a closing pressure chamber, so that the closing piston can be acted upon by fuel pressure, to attain a force acting on the closing piston in the closing direction. The closing pressure chamber and the return chamber are formed by a common closing-pressure return chamber, in which all the portions of the chamber communicate permanently with one another for exchanging fuel. A pressure chamber is provided for supplying injection openings with fuel and for acting upon the closing piston with a force acting in the opening direction. A high-pressure chamber communicates with the high-pressure fuel source in such a way that in the high-pressure chamber, aside from pressure fluctuations, at least the fuel pressure of the high-pressure fuel source can be constantly applied. The pressure chamber and the high-pressure chamber are formed by a common injection chamber, and all the portions of the injection chamber communicate permanently with one another for exchanging fuel. 
   German Patent Disclosure DE 102 47 903.8 relates to a pressure-boosted fuel injection device with a control line embodied on the inside. The fuel injection device communicates with a high-pressure source and includes a multi-part injector body. Received in the injector body is a pressure booster, which can be actuated via a differential pressure chamber and whose pressure booster piston divides a work chamber from the differential pressure chamber. The fuel injection device can be actuated via a switching valve. A pressure change in the differential pressure chamber of the pressure booster is effected via a central control line that extends through the pressure booster piston. The switching valve can be embodied as either a magnet valve or a servohydraulic 3/2-way valve. 
   OBJECT AND SUMMARY OF THE INVENTION 
   With the embodiment proposed according to the invention, it becomes possible to control a servo piston of a servo valve with the diversion quantity of fuel from the return chamber of the pressure booster. The quantity of fuel flowing out of the return chamber of the pressure booster must be both depressurized and diverted into the return, so that an injection can be made. With the embodiment of the invention, filling of the control chamber of the servo valve with precisely this quantity of fuel diverted from the return chamber of the pressure booster is possible, so that in the fuel injector configured according to the invention, the servo valve control does not cause any additional loss of fuel quantity. 
   The valve provided on the fuel injector proposed according to the invention still has no leakage at the servo piston in the state of repose, and as a result the injector efficiency is improved, and in particular the guide lengths of the servo piston can be kept short. In an advantageous version, the servo valve, which contains the servo piston, can be designed as a 3/2-way seat-to-seat valve, in which a sealing seat—to name one example—can be embodied as a flat seat, and a housing comprising multiple housing parts can be employed. Embodying the 3/2-way valve as a 3/2-way seat-to-seat valve offers the opportunity of completely eliminating the problems of sealing and tolerances that occur in slide seals with short overlapping lengths. 
   The invention will be better understood and further objects and advantages thereof will become more apparent from the ensuing detailed description of preferred embodiments taken in conjunction with the drawings, in which: 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  shows a first exemplary embodiment of a servo valve according to the invention which is assigned to a fuel injector and has a leakage-free servo piston, with control via the return chamber of a pressure booster; and 
       FIG. 2  shows a further exemplary embodiment of the servo valve proposed according to the invention, with a conical sealing seat. 
   

   DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   In  FIG. 1 , an exemplary embodiment of a servo valve with a leakage-free servo piston is shown, which is associated with a fuel injector with a pressure booster; the servo valve is triggered via the return chamber of the pressure booster. The fuel injector  18  shown in  FIG. 1  is subjected to fuel that is at high pressure via a high-pressure line  2  that extends from a pressure source  1  embodied as a high-pressure collection chamber. The fuel flowing to the fuel injector  18  via the high-pressure line  2  acts on a work chamber  5  of a pressure booster  3 . The work chamber  5  is acted upon permanently by the fuel, which is at high pressure, of the high-pressure source  1 . Via a piston  4  of the pressure booster  3 , the work chamber  5  is divided from a differential pressure chamber (return chamber)  6 . An end face  20  of the pressure booster piston  4  acts upon a compression chamber  9  of the pressure booster  3 . The booster piston  4  of the pressure booster  3  is acted upon via a restoring spring  8 , which is braced on a support disk  7  that is let into the injector body  19  of the fuel injector  18 . 
   From the differential pressure chamber  6  (return chamber) of the pressure booster  3 , an overflow line  10 , which contains a first throttle restriction  11 , leads to a control chamber  12 . Received inside the control chamber  12  for an injection valve member  14  is a spring element  13 , which is braced on a boundary wall of the needle control chamber  12  and acts upon a face end of the injection valve member  14 . The injection valve member  14  can be embodied as a nozzle needle, for instance. In addition, the compression chamber  9  of the pressure booster  3  and the control chamber  12  communicate with one another via a line that contains a second throttle restriction  15 . 
   The injection valve member  14  is surrounded by a nozzle chamber  16 . The injection valve member  14  has a pressure step, which is engaged by the fuel at high pressure flowing into the nozzle chamber  16  when the injection valve member  14  is actuated in the opening direction. The compression chamber  9  of the pressure booster  3  communicates with the nozzle chamber  16  via a nozzle chamber inlet  17  that carries high pressure. 
   From the differential pressure chamber  6  (return chamber) of the pressure booster  3 , a diversion line  21  leads to a servo valve, identified by reference numeral  22 . The servo valve  22  is received in a valve body  28  that is located above the fuel injector  18 . Via the diversion line  21 , fuel diverted from the differential pressure chamber  6  (return chamber) flows into a first hydraulic chamber  29  of the valve body  28 . The valve body  28  surrounds a servo valve piston  23 , which in the exemplary embodiment shown in  FIG. 1  has a through conduit  23 . 1 . Via the through conduit  23 . 1  that connects the first hydraulic chamber  29  with a control chamber  36 , the control chamber  36  of the servo valve  22  is filled with fuel. A pressure relief of the control chamber  36  of the servo valve  22  is effected by actuation of a relief valve  33 , indicated here only schematically. From the relief valve  33 , a first return  32  leads to a fuel reservoir, not shown in further detail here. 
   The servo valve piston  23  of the servo valve  22  has a face end  25  which defines the control chamber  36  of the servo valve  22 . A throttle restriction  24  is integrated with the through conduit  23 . 1  of the servo valve piston  23 , as shown in FIG.  1 . 
   From the high-pressure line  2  that supplies the work chamber  5  of the pressure booster  3  with fuel that is at high pressure, a branch leads through the valve body  28 , and by way of it a second hydraulic chamber  30  of the servo valve  22  is subjected to fuel that is at high pressure. As shown in  FIG. 1 , a sealing edge  26  is embodied on the underside of the servo valve piston  23  having the through conduit  23 . 1 , and this sealing edge seals off an outflow control chamber  35 , which discharges into a second return  34  on the low-pressure side of the fuel injector  18 . The servo valve piston  23  furthermore has a portion of mushroom-shaped configuration that cooperates with a sealing edge  27  embodied in the valve body  28  and with it, upon contact, forms a sealing seat  31 . Both the sealing edge  26  embodied on the underside of the servo valve piston  23  having the through conduit  23 . 1  and the sealing edge  27  embodied on the valve body  28  can be embodied as either a flat seat, conical seat, ball seat, or slide edge. In the illustration in  FIG. 1 , the sealing edge  27  is embodied as a conical seat. 
   MODE OF OPERATION 
   In the state of repose of the fuel injector  18 , the sealing edge  26  is closed as shown in  FIG. 1 ; that is, the second return  34  is closed. Conversely, in the state of repose the sealing seat  31  is open, and the servo valve body  23  with the through conduit  23 . 1  is guided in a manner proof against high pressure in the valve body  28  of the servo valve  22 ; that is, no fuel flows between the control chamber  36  and the second hydraulic chamber  30 . Within this guide region, in the state of repose, system pressure prevails both on the side of the control chamber  36  and on the side of the second hydraulic chamber  30 , so that no leakage flow to the return occurs. The entire region of the servo piston  23  with the through conduit, that is, the control chamber  36 , first and second hydraulic chambers  29  and  30 , and the sealing seat  31 , is acted upon by system pressure, which is sealed off from the second return  34  in leakage-free fashion by the sealing edge  26  that is moved into its closing position. 
   In the state of repose, the pressure booster  3 , the differential pressure chamber  6  (return chamber), via the opened sealing seat  31 , and the high-pressure supply line  2  that discharges into the work chamber  5  are acted upon by system pressure. In this case, the piston  4  of the pressure booster  3  is in pressure equilibrium, and no pressure boosting occurs. 
   For triggering the pressure booster  3 , the differential pressure chamber  6  (return chamber) of the pressure booster  3  is pressure-relieved. For the pressure relief, first the relief valve  33  is activated, that is, opened; as a result, the control chamber  36  that actuates the servo valve  22  is pressure-relieved into the first return  32 . The servo valve piston  23  with the through conduit moves upward as a result of the pressure force that engages the underside of the mushroom-shaped portion in the first hydraulic chamber  29  and thus opens the sealing edge  26 , while conversely the sealing seat  31  is closed. The sealing edge  26  or the second return  34  or both are designed such that even in the opened state, a slight residual pressure is preserved in the first hydraulic chamber  29 , thus assuring that the servo valve piston  23  will remain in its open position and that the sealing seat  31  will remain securely closed. The control flow that flows out via the relief valve  33  into the first return  32  and via the throttle restriction  24  and the open sealing edge  26  into the second return  34  is not a lost quantity, since it is taken from the differential pressure chamber  6  (return chamber) of the pressure booster  3 , and this quantity flows to the second return  34  via the sealing edge  26  every time the pressure booster  3  is activated. 
   When the servo valve piston  23  with the through conduit is open, the differential pressure chamber of the pressure booster is disconnected from the pressure level prevailing in the high-pressure source  1 . A pressure relief of the differential pressure chamber  6  (return chamber) takes place via the diversion line  21  into the second return  34 . The pressure in the compression chamber  9  is raised in accordance with the inward motion of the end face  20  of the booster piston  4 , as a function of the boosting ratio of the pressure booster  3 , and via the nozzle chamber inlet  17 , it is delivered to injection openings  45  into the combustion chamber  46  of an internal combustion engine. Because of the pressure step embodied on the injection valve member  14 , the injection valve member  14  opens when pressure is exerted on the nozzle chamber  16  and uncovers the injection openings  45 , and the injection begins. When the injection valve member  14  is completely open, the line that contains the compression chamber  9  and the needle control chamber  12  and a second throttle restriction  15  is closed, so that during the injection event, no lost flow occurs. For damping the opening speed of the injection valve member  14 , a separate damping piston can be used. Filling of the compression chamber  9  can be alternatively effected via a check valve, instead of via a line that contains a second throttle restriction  15 . 
   For terminating the injection event, the relief valve  33  is closed. By an overflow of fuel from the first hydraulic chamber  29  via the through conduit  23 . 1  of the servo valve piston  23 , the pressure level prevailing in the first hydraulic chamber  29  builds up in the control chamber  36 . Since by design a residual pressure level remains in the first hydraulic chamber  29 , a pressure force acting in the closing direction and generated in the control chamber  36  is established, which acts upon the face end  25  of the servo valve piston  23  having the through conduit  23 . 1 . The servo valve piston  23  with the through conduit  23 . 1  moves downward into its outset position, whereupon the sealing edge  26  is returned to its closing position relative to the outflow control chamber  35 , and the sealing seat  31  on the valve body  28  of the servo valve  22  is opened again. To reinforce the motion of the servo valve piston  23  with the through conduit  23 . 1 , it is entirely possible for additional spring elements, which however are not shown in  FIG. 1  to be received in the valve body  28  of the servo valve  22 . 
   In the work chamber  5  of the pressure booster  3  and in the control chamber  36  of the servo valve  22 , a pressure buildup takes place via the open sealing seat  31 , to the pressure level prevailing in the high-pressure source  1 . Because of this, the pressure in the compression chamber  9  of the pressure booster  3  and thereupon the pressure prevailing in the nozzle chamber  16  both drop, so that the spring  13  disposed in the control chamber  12  moves the injection valve member  14  into its closing position, and the injection openings  45  that discharge into the combustion chamber  46  of the self-igniting engine are closed. 
   The sealing edge  26  of the servo valve piston  23  and the sealing edge  27 , acting as the sealing seat  31 , embodied on the valve body  28  can be embodied in manifold ways. Combinations of a flat seat, conical seat, ball seat or slide edges can be achieved. In order to design both the sealing edge  26  and the sealing edge  27  embodied in the valve body  28  as sealing seats, the valve body  28  is constructed in multiple parts, for instance in two parts, these being the components  28  and  28 . 1 . If the sealing edge  26  is embodied as a flat seat, for instance, then production tolerances in terms of an axial offset of the two valve body components  28  and  28 . 1  can very easily be compensated for. The sealing edge  26  is acted upon by a strong hydraulic sealing force, generated in the control chamber  36  of the servo valve  22 , so that tightness of the sealing edge  26 , which seals off the outflow control chamber  35  from the second return  34 , at the production precision levels that are attainable at present, is assured even for fuel at extremely high pressure. 
   From the exemplary embodiment shown in  FIG. 2 , a servo valve piston of a servo valve can be seen, whose sealing edge on the low-pressure side is embodied as a conical seat. In contrast to the exemplary embodiment shown in  FIG. 1 , of a fuel injector  18  with a servo valve  22 , which includes a servo valve piston  23  with a through conduit  23 . 1 , in the illustration in  FIG. 2  the servo valve piston  43  of the servo valve  22  is embodied without such a through conduit  23 . 1 . Moreover, the valve body  28  that receives the servo valve  22  is embodied in one piece. To facilitate assembly, the servo valve piston  43  in the exemplary embodiment shown in  FIG. 2  has a slide portion  47 , which is embodied with the same diameter as the head region of the servo valve piston  43 , whose face end  25  defines the control chamber  36  of the servo valve  22 . In a distinction from what is shown in  FIG. 1  filling of the control chamber  36  is effected via a separate line, branching off from the diversion line  21 , that contains a throttle restriction  44  toward the valve housing. 
   The slide portion  47  is embodied with an axial length adapted to the servo valve piston  43  such as to enable an overlap of the slide edge  40 , embodied in the one-piece valve body  28  of the servo valve  22 , upon closure. Besides a slide seal edge  40 , a sealing face can also be embodied here. The sealing force on the servo piston  43  is adjusted via a pressure face facing the diversion chamber  35 . When a sealing face is used, an optimal layout of the pressure per unit of surface area is possible, and as a result both adequate tightness and low wear can be attained. In a distinction from the servo valve piston  23  with the through conduit of  FIG. 1 , a sealing edge  41  that closes the outlet of the diversion chamber  35  to the second return  34  is embodied as a conical sealing seat. The mode of operation of the servo valve  22  in the second exemplary embodiment of  FIG. 2  is equivalent to that of the fuel injector  18  and the servo valve  22  that have already been described in conjunction with FIG.  1 . The relief valve  33  for relieving the pressure of the control chamber  36  of the servo valve  22  can be embodied as a 2/2-way valve or as a 3/2-way valve. Besides the variant embodiment as a magnet valve shown in  FIG. 2 , the relief valve  33  can also be embodied as a piezoelectric actuator. 
   Upon pressure relief of the differential pressure chamber  6  (return chamber) of the pressure booster  3 , in the exemplary embodiment shown in  FIG. 1  an overflow of fuel takes place via the diversion line  21  into the first hydraulic chamber  29 , and from there, via the through conduit embodied in the servo valve piston  23 , filling of the control chamber  36  of the servo valve takes place. In the exemplary embodiment shown in  FIG. 2 , upon pressure relief of the differential pressure chamber  6  (return chamber) of the pressure booster  3 , filling of the first hydraulic chamber  29  and of the control chamber  36 , containing a stop  42  for the face end  25  of the servo valve piston  43 , takes place in parallel, via two line segments branching off from the diversion line  21 . In the exemplary embodiment of  FIG. 1 , a throttle restriction  24  is provided in the through conduit of the servo valve piston  23 , and in the exemplary embodiment of  FIG. 2  a throttle restriction  44  toward the valve body is likewise disposed in the line segment by way of which the control chamber  36  of the servo valve  22  is filled. The pressure relief of the control chamber  36  of the servo valve  22  takes place analogously to  FIG. 1 , via an actuation of the switching valve  33  and a diversion of a control quantity from the control chamber  36  into the first return  32 . 
   In the exemplary embodiment shown in  FIG. 2 , the high-pressure supply line  2  extending from the high-pressure source  1  (common rail) into the work chamber  5  of the pressure booster  3  discharges directly into the work chamber  5  of the pressure booster  3 . From there, a line branches off that enables filling of the second hydraulic chamber  30  of the servo valve  22 . The construction of the fuel injector  18  with regard to the components contained in the injector body  19  is equivalent to the construction that has already been described in conjunction with the first exemplary embodiment of the fuel injector  18  according to the invention, and its valve body  19 . 
   Instead of the conical sealing seat  41 , shown in the exemplary embodiment of  FIG. 2 , on the underside of the servo valve piston  43 , it is readily possible to embody this seat as a flat seat, ball seat, or slide edge, depending on the sealing tolerances attainable by the production technology employed. The sealing force acting on the sealing edge  26  (of  FIG. 1 ) or the conical sealing seat  41  (of  FIG. 2 ) is adjusted by way of the pressure level generated in the control chamber  36  of the servo valve  22 . The higher this pressure level, the higher the pressure force is that is established above the outflow control chamber  36  in the direction of the second return  34 . 
   The foregoing relates to preferred exemplary embodiments of the invention, it being understood that other variants and embodiments thereof are possible within the spirit and scope of the invention, the latter being defined by the appended claims.

Technology Classification (CPC): 5