Abstract:
A device, for the translation of a displacement of an actuator, in particular for an injection valve, essentially comprises two counter-displaceable pistons, coupled together by means of a translational chamber in a play-free manner. The translation chamber is filled with a translation medium and is connected to an equalization chamber by means of a sealing gap. The sealing gap only equalizes pressure differences between the translation chamber and the equalization chamber which are of long duration. One of the two pistons is pre-tensioned in a starting position by means of an externally arranged spring. A reduction in the dead volume between the pistons is possible as a result of the arrangement of the spring outside the piston.

Description:
CROSS REFERENCE TO RELATED APPLICATION 
     This application is a continuation of copending International Application No. PCT/DE02/04465 filed Dec. 5, 2002 which designates the United States, and claims priority to German application no. 101 62 045.4 filed Dec. 17, 2001. 
    
    
     TECHNICAL FIELD OF THE INVENTION 
     The invention relates to a device for the translation of a displacement of an actuator. 
     DESCRIPTION OF THE RELATED ART 
     Injection valves such as piezoelectrically operated injection valves use an actuator with a relatively small control displacement. So that an injection needle or a servo valve for controlling an injection needle can be correctly actuated despite the small displacement of the piezoelectric actuator, it is necessary to translate the displacement of the actuator. Appropriate translation devices are used for this translation. 
     A hydraulic device for the translation of an actuator displacement is known from document DE 19 962 177 A1. The device has a first piston element which is solidly connected to an actuator. A second piston element, which is connected to a control element, is also provided. A hydraulic chamber is provided between the first piston element and the second piston element. A storage chamber, which is connected to the hydraulic chamber by means of a throttle gap, is also formed. The storage chamber includes a pressurized storage chamber area, the boundaries of which are elastically formed. The area boundaries are marked by bellows arrangements which are pre-tensioned by a pre-tensioning spring opposite the housing of the injection valve. Pre-tensioning the storage chamber area creates pressure in the storage chamber, ensuring reliable filling of the hydraulic chamber. 
     From document DE 19 950 760 A1 there is known to be a fuel injection valve which has a piezoelectric or magnetostrictive actuator. 
     Between the actuator and a valve needle is a ram device provided with two reciprocating pistons moving in counter-motion to one another. The ram device is hermetically sealed relative to a valve interior. The first reciprocating piston is effectively connected to the actuator and takes the form of a hollow cylinder which is open at one end and the opening of which is modified by the actuator. The second reciprocating piston is located in the cylinder opening. The first reciprocating piston itself is located in a hollow, cylindrical housing. A translation chamber is formed between one end surface of the housing and the first and second pistons. The second piston is effectively connected to an injection needle. A piston chamber is formed between the first piston and the second piston. A second bellows is fastened in leak-proof fashion around the housing and a piston rod from the second piston, thereby forming a first pressure chamber. In the same way a first bellows is fastened in leak-proof fashion around the housing and the first piston, thereby forming a second pressure chamber. The piston chamber is connected to the first and second pressure chambers by means of openings. Located in the piston chamber is a tensioning spring which pre-tensions the first and second pistons in opposing directions. The disclosed injection valve is relatively large due to the arrangement of the tensioning spring. Moreover the piston chamber has a relatively large dead volume. The dead volume gives rise to a restriction in the motional dynamics of the first and second pistons. 
     Due to an unpublished patent application submitted by the applicant, with the title “Geschlossenes Hydrauliksystem” (“Closed hydraulic system”) and the file number 10046323.1, a device for the translation of a displacement of an actuator is known. In this arrangement also, a tensioning element is arranged in the piston chamber between a first and a second piston. The dead volume in the piston chamber is relatively large in this embodiment also. The relatively large dead volume gives rise to adverse effects on the motional dynamics of the first and second pistons. 
     SUMMARY OF THE INVENTION 
     The object of the invention is to provide a device for the translation of a displacement of an actuator, comprising a small amount of dead volume in the piston chamber. 
     The object of the invention can be achieved by a device for the translation of a displacement of an actuator, in particular for an injection valve, comprising a housing, wherein a first and a second piston are held in a movable fashion, the first piston, the second piston and the housing form the boundaries of a translation chamber, the translation chamber is filled with translation medium and the position of the first piston determines the position of the second piston, the translation chamber is connected to an equalisation chamber by means of a hydraulic line, the hydraulic line equalises only pressure differences of long duration between the equalisation chamber and the translation chamber, the equalisation chamber is bounded by a first and/or second bellows, a sealing gap is formed between the housing and the second piston and is sealed by means of a third bellows, a means of tensioning is provided and this pre-tensions the second piston in a rest position, and wherein the means of tensioning is fitted in the form of a tensioning spring between the housing and the second piston. 
     The object can also be achieved by a device for the translation of a displacement of an actuator comprising a housing, a first and a second piston which are held in a movable fashion wherein the position of the first piston determines the position of the second piston and which form together with the housing the boundaries of a translation chamber, a translation medium which fills the translation chamber which is connected to an equalisation chamber by means of a hydraulic line, wherein the hydraulic line equalises only pressure differences of long duration between the equalisation chamber and the translation chamber, wherein the equalisation chamber is bounded by a first and/or second bellows, a sealing gap formed between the housing and the second piston which is sealed by means of a third bellows, and a means of tensioning which pre-tensions the second piston in a rest position, wherein the means of tensioning is fitted in the form of a tensioning spring between the housing and the second piston. 
     The housing may have a first chamber with an end wall. The first piston can be located in the piston chamber. The first piston may have a second piston chamber. The second piston may be located in the second piston chamber. A drill hole can be formed in the end wall of the housing, through which a piston rod of the second piston is fed. The translation chamber can be formed between the end wall of the housing and two working faces of the first and second pistons. The first and second pistons may form the boundaries of a further chamber, and the further chamber can be connected to the equalisation chamber by means of a hydraulic line. The tensioning spring may lie on a bearing surface of the housing, a supporting ring can be provided and can be attached to the piston rod, and the tensioning spring can be fixed between the supporting ring and the housing. The supporting ring can be in the form of a sleeve with a supporting rim, and the supporting ring can be connected to the piston rod by means of a safety ring. A second tensioning spring can be provided, and the second tensioning spring can be fixed between the housing and a piston rod of the first piston. A second tensioning spring can be provided, and the second tensioning spring can be fixed between the first and second bellows and the piston rod of the first piston. The first and the second bellows can be connected to a sleeve-shaped connecting ring. The connecting ring may have a surrounding bearing edge opposite the connection side of the first and second bellows. The second tensioning spring may rest on the said bearing edge. A second supporting ring can be in the form of a sleeve with a supporting rim, and the second supporting ring can be connected to the piston rod of the first piston by means of a safety ring. The first piston chamber of the housing in the open area may have a surrounding edge area. On the edge area a ring can be fastened all the way round in leak-proof fashion. The first bellows can be welded to an edge area all the way round in leak-proof fashion by means of the ring. The second edge area of the first bellows can be connected to a connecting ring. The second bellows can be connected all the way round in leak-proof fashion to the second piston by means of a first edge area, and the second edge area of the second bellows can be connected to the connecting ring. The ring may have a sealable drill hole for filling the equalisation chamber. The second piston may have a drill hole running from a front end which forms the boundary of the piston chamber to the area which houses the third bellows for closing a third sealing gap formed between the second piston and the housing. 
     One advantage of the invention stems from the fact that the dead volume in the piston chamber is reduced. The advantage of the invention is achieved in that the tensioning element for pre-tensioning the second piston is arranged outside the piston chamber. Since the tensioning element is arranged outside the piston chamber, the piston chamber can be significantly smaller. Due to the smaller piston chamber, altogether greater dynamics are achieved in the translation of the motion of the first piston and on the second piston. 
     In a preferred embodiment of the invention the means of tensioning provided is a tensioning spring that is fixed between the housing and a supporting ring. The supporting ring is fastened to a piston rod of the second piston. The arrangement of a supporting ring provides a simple and reliable bearing surface for the tensioning spring. 
     Preferably the supporting ring takes the form of a sleeve in which a supporting rim is formed. The tensioning spring grips the supporting rim. The supporting ring is connected to the piston rod by means of a locking plate. Using a sleeve-shaped supporting ring prevents the tensioning spring from becoming misshapen. In addition the fashioning of a supporting rim provides a secure bearing surface for the tensioning spring. Furthermore the use of a locking plate is a safe and simple technique for connecting the supporting ring and the piston rod. Reliable functioning of the translation device together with excellent long-term stability is thus achieved. 
     The preferred embodiment is provided with a second tensioning spring which is likewise arranged outside the piston chamber and is fixed between the housing and a piston rod of the first piston. Pre-tensioning of the first piston in the opposite direction to the pre-tensioning of the second piston is thus also achieved. By this means a starting position for the first piston is reliably defined. This therefore makes it among other things unnecessary for the first piston to be solidly connected to an actuator. 
     In a preferred embodiment the second tensioning spring is arranged outside the housing, where it is fixed between the first and second bellows and the piston rod of the first piston. By this means not only is the piston rod pre-tensioned but also a pressure is created in the equalization chamber bounded by the first and second bellows. 
     In a further preferred embodiment the piston chamber is hydraulically connected by means of a drill hole to a sealed area which is arranged outside the housing and preferably sealed by a bellows that is connected in leak-proof fashion around the housing and the second piston. By this means the piston chamber can be quickly emptied. In a further preferred embodiment the piston chamber is also hydraulically connected to the equalization chamber by means of a drill hole. This connection to the equalization chamber also enables the fluid to escape quickly from the piston chamber. These arrangements enable the first piston to move towards the second piston without any significant counter-force. 
     A further advantageous embodiment consists in sealing the housing by means of a ring, with a piston rod of the first piston passing through the opening of the ring. The said ring preferably has a sealable drill hole for filling the device with fluid. The invention will be explained in greater detail with the aid of the FIGURE. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWING 
       The FIGURE is a diagram of a cross-section through the device to which the invention relates for the translation of a displacement of an actuator to a control element. The translation device to which the invention relates can be used for any type of actuator and control element, but is particularly suitable for use in an injection valve, for instance for controlling a servo valve with the aid of a piezoelectric actuator. 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     There is a first piston  1  in the form of a sleeve which is open at one end. The sleeve-shaped part of the piston forms a piston chamber  3  in which a second piston  2  is located. The first and second pistons  1 ,  2  form the boundaries of the piston chamber  3 . The first piston  1  is itself located in a cylinder-shaped chamber  48  of a housing  4  which has an end surface  5  at the front end of the first piston  1 . In the end surface  5  is an opening  6  through which a piston rod  7  of the second piston  2  is led. The piston rod  7  has a smaller diameter than the second piston  2 . The piston rod  7  has a ring-shaped shoulder  8  and thus changes to the wider diameter of the second piston  2 . A translation chamber  10  is formed between the end surface  5 , the shoulder  8  and a ring-shaped front end  9  of the first piston  1 . The translation chamber  10  is hydraulically connected to the piston chamber  3  by means of a first sealing gap  11  which is formed between a side wall of the second piston  2  and an inner wall of the first piston  1 . The piston chamber  3  is bounded by an end surface  47  of the first piston  1  and a front end  49  of the second piston  2 . 
     The translation chamber  10  is also connected to a further sealing gap  13  by means of a second sealing gap  12  which is formed between the outer wall of the first piston  1  and the inner wall of the housing  4 . The further sealing gap  13  is formed between a sealing ring  14  and a first section  16  of a second piston rod  17 . The first piston  3  has a second shoulder  15  and thus changes to the first section  16  of the second piston rod  17 . The first piston  16 , which is basically cylinder-shaped, has a third shoulder  21  and thus changes into a second section  18  of the second piston rod  17 . The second section  18  of the second piston rod  17  is basically cylinder-shaped and has a smaller diameter than the first section  16 . 
     All round the sealing ring  14  is a ring-shaped groove  20  which is formed in the area at the outer edge of the sealing ring  14  and is associated with a ring-shaped front end  19  of the housing  4 . Preferably the internal diameter of the sealing ring  4 , which is tapered due to the ring-shaped groove  20 , is matched to the internal diameter of the cylinder-shaped recess of the housing  4 . This ensures a good fit and therefore a good seal between the housing  4  and the sealing ring  14 . The sealing ring  14  may for example be connected to the housing  4  by means of a leak-proof welding seam running all the way round. 
     In the area of the third shoulder  21  a first, basically sleeve-shaped bellows  22  is fastened all the way round in a leak-proof fashion by means of a first end area to the third shoulder  21 . The first bellows  22  is preferably made from a metallic material and therefore preferably connected to the metallic second piston  2  in a leak-proof fashion by means of a welding seam running all the way round. A second end of the first bellows  22  is connected all the way round in a leak-proof fashion to a connecting ring  23 . The second section  18  of the second piston rod  17  passes through the opening of the connecting ring  23 . 
     The connecting ring  23  has a fourth shoulder  24 , which causes the diameter of the connecting ring  23  to become larger. In the area of the fourth shoulder  24  a second, basically sleeve-shaped bellows  25  is connected all the way round in a leak-proof fashion to the connecting ring  23 . The second bellows  25  is connected all the way round in a leak-proof fashion in the area of its other edge, to a front end of the sealing ring  14  turned towards the connecting ring  23 . By this means an equalization chamber  26  is formed between the first and second bellows  22 ,  25  and the connecting ring  23 . 
     The equalization chamber  26  is hydraulically connected to the translation chamber  10  by means of the further sealing gap  13  and the second sealing gap  12 . The hydraulic connection is so designed that pressure differences between the translation chamber  10  and the equalization chamber  26  are only equalized if the pressure differences persist for a minimum length of time. The sealing gaps and the chosen geometry define the minimum time in such a way that the time needed to translate a force from the first piston to the second piston must be exceeded before pressure equalization takes place. This ensures that a force can be translated from the first piston to the second piston  1 ,  2  virtually without loss, whereas pressure differences which are of long duration are equalized. By this means the translation chamber  10  can be completely filled even in the presence of temperature fluctuations or wear and tear. This ensures that the translation chamber  10  is always completely filled with a translation fluid such as hydraulic oil. 
     A first drill hole  27 , leading from the end surface  47  which forms the boundary of the piston chamber  3  to the further sealing gap  13 , is formed in the first piston  1 . This creates a hydraulic connection linking the equalization chamber  26  to the piston chamber  3 . The said hydraulic connection enables pressure to be quickly equalized between the equalization chamber  26  and the piston chamber  3 . 
     In the end area of the second piston rod  17  is a safety groove  28  in which a locking plate  29  is fastened. Clamped to the locking plate  29  is a second connecting ring  30 . A first spring  31  is fixed between the second and first connecting rings  30 ,  23 . The first spring  31  applies a pre-tensioning force to the first connecting ring  23  and thence to the first and second bellows  22 ,  25 . This has the effect of pressurizing the translation fluid in the equalization chamber  26 . 
     The sealing ring  14  has a continuous second drill hole  32 . Translation fluid can be poured from outside via this second drill hole  32  into the third sealing gap  13  and the volume hydraulically connected to the third sealing gap  13  can be filled. When all volumes hydraulically connected to the third sealing gap  13  have been filled, the second drill hole  32  is closed by means of a closure  33 . In the typical embodiment shown the closure  33  is in the form of a sphere. 
     The housing  4  is tapered in its external diameter in the area of the first piston rod  7  by means of a shoulder on a ring-shaped part  34  with a smaller external diameter. The ring-shaped part  34  surrounds the first piston rod  7 . The first piston rod  7  extends a predetermined distance towards the ring-shaped part  34 . The ring-shaped part  34  has a ring-shaped, second front end  35  which basically is arranged vertically to the lengthways direction of the first piston rod  7 . At a predetermined distance from the ring-shaped part  34  is a third sealing ring  36  connected all the way round in a leak-proof fashion to the piston rod  7 . The third sealing ring  36  has a ring-shaped, third front end  37  which is turned towards the ring-shaped part  34 . Between the ring-shaped part  34  and the third sealing ring  36  is a third bellows  38  which is basically designed in the form of a cylinder and fastened all the way round in a leak-proof fashion by means of an end area to the second front end of the ring-shaped part  34  and by means of the other end area to the third front end  37  of the third sealing ring  36 . By this means a third sealing gap  50 , which is formed between the housing  4  and the piston rod  7  and connected to the translation chamber  10 , is reliably sealed. 
     In the end area of the piston rod  7  is a second safety groove  39  in which a second locking plate  40  is fixed. A fourth connecting ring  41  is clamped to an inner side of the second locking plate  40 , which is turned towards the housing  4 . A second spring  42  is fixed between the fourth connecting ring  41  and the housing  4 . The second spring  42  lies on a fourth front end  43  of the housing  4 , formed by the shoulder of the housing  4 , in which the housing  4  changes from a fairly large external diameter to the ring-shaped part  34  with a smaller external diameter. 
     The second piston  2  has a third drill hole  44  created centrally at the front end  49  of the second piston  2 , going from the front end  49  to the piston rod  7  in an area at the edge of the piston rod  7 , and arranged at the same height as the third bellows  38 . This creates a hydraulic link between the piston chamber  3  and an equalization chamber  45  bounded by the piston rod  7  and the third bellows  38 . In a simple embodiment the piston chamber is in the form of a blind hole boring with a centrally drilled blind hole  46 . The blind hole  46  is hydraulically connected to the third sealing gap  13  via the first drill hole  27 . 
     The translation device to which the figure relates works as follows: The volumes which are formed in the translation device and hydraulically connected to the translation chamber  10  are completely filled with a fluid medium which is preferably incompressible. In a rest position the first piston  1  is held in a starting position with pre-tensioning by the first spring  31 . The starting position may be set for instance by positioning the first piston with the second shoulder  15  at the connecting ring  14 . The second piston  2  is at rest in a starting position in which the second piston  2  is pre-tensioned by the second spring  42 . The rest position may be determined for instance by positioning the second piston  2  with the shoulder  8  at the end surface  5  of the housing  4 . The piston rods  7 ,  17  of the first and second pistons  1 ,  2  are pre-tensioned in the opposite direction in the rest position of the housing  4 . The volume formed between the pistons  1 ,  2  and the housing  4 , and between the bellows  22 ,  25 , and between the third bellows  38  and the piston rod  7 , is filled with a translation medium, in particular a hydraulic fluid. Filling takes place via the second drill hole  32 , which is then closed with the aid of the closure  33 . Due to the pre-tensioning of the equalization chamber  26  via the first spring  31  a specific pressure is present in the transmission medium even in the idle state. The idle state of the first and the second piston is preferably also defined in that the first and the second piston rods  7 ,  17  are clamped to an actuator or to a control element, giving a play-free effective connection between the actuator and the control element. 
     The actuator may be designed as a piezoelectric actuator for example. If the actuator is then activated, it moves the first piston  1  in the direction of the housing  4 . Due to the hydraulic coupling of the second piston  2  to the first piston  1  via the translation chamber  10 , the second piston  2  and the piston rod  7  of the second piston  2  are likewise moved away from the housing, counter to the direction of movement of the first piston  1 . If the piston rod  7  is effectively connected to an injection needle, then the movement of the piston rod  7  may be made to raise the injection needle from a leak-proof seating so that fuel can be injected into an internal combustion engine. In another typical embodiment a servo valve is opened or closed by the action of the second piston so that a pressure change can affect an injection needle and cause the injection needle to be lifted from a leak-proof seating. 
     If the supply of current to the actuator is interrupted, no further force acts upon the second piston rod  17  of the first piston  1 . Consequently the second piston rod  17  of the first piston  1  is moved away from the housing  4  by the pre-tensioning force of the first spring  31 . Likewise the second piston  2  is moved back to the starting position by the second spring  42 . 
     On the one hand this approach ensures that the displacement of the first piston is reliably translated into a corresponding displacement of the second piston in the opposite direction, and on the other hand it ensures reliable positioning of the first and the second piston rods on an actuator or on a control element. Positioning is ensured in that appropriate spring media  31 ,  42  are provided and in that activation of the actuator is immediately translated into a corresponding activation of the second piston, since the translation chamber  10  is always reliably filled with translation medium. 
     Because of the arrangement of the second spring  42  outside the housing  4  and in particular outside the piston chamber  3 , the volume in the piston chamber  3  can be kept low. Due to the low volume of the piston chamber  3  the total volume filled with translation medium is reduced. Superfluous dead volume in the translation device is thereby reduced. The function of the translation device is thus improved. 
     Preferably the translation medium in the equalization chamber  26  is pressurized by means of the arrangement of the first spring  31 . This ensures that the translation chamber  10  is securely and quickly filled with translation medium. This in turn reliably ensures a play-free coupling between the first and the second pistons  1 ,  2  and a corresponding actuator or control element. Since the first spring  31  is coupled to the piston rod  17  of the first piston  1 , the pressure in the equalization chamber  26  is increased when the first piston  1  is activated by the actuator. This causes the total external pressure on the translation chamber  10  to be increased when the translation device is activated, so that the escape of translation medium from the translation chamber  10  is impeded. This has the advantage that the sealing gaps which the translation chamber  10  connects to the other translation medium volumes need not be sealed so precisely in order to prevent a transient escape of translation medium from the translation chamber. The translation device thus becomes more cost-effective to manufacture.