the invention is shown below using the example of an injection valve 1 . however , the use of the transmission device according to the invention is not restricted to injection valves , as the transmission device according to the invention can be used in diverse technical fields to transmit a displacement of an actuator . fig1 shows an injection valve 1 with an actuator 2 mechanically linked to an injection valve needle 4 via a transmission device 3 . the actuator 2 is for example configured as a piezoelectric actuator and the transmission device 3 preferably has a translation function , so that a displacement of the actuator 2 is transmitted in the direction of the injection needle 4 by the transmission device 3 in order to effect a larger displacement of the injection needle 4 . the injection needle 4 is assigned to injection holes of the injection valve . as a function of the displacement of the actuator 2 , the injection needle 4 releases the injection holes , so that fuel is injected into an internal combustion engine via the injection holes . depending on the embodiment , the transmission device 3 can also have an inverse function , so that the setting element that is mechanically linked to the injection needle 4 is withdrawn from the injection needle 4 when the actuator 2 is displaced in the direction of the injection needle 4 . instead of the translation function , the transmission device 3 can also have a pure transmission function , the displacement of an actuator being transmitted in order to effect a corresponding displacement of the injection needle . fig5 shows a more precise representation of the transmission device 3 . a first piston 6 is provided in the form of a sleeve that is open on one side . the sleeve - shaped part of the piston delimits a first transmission chamber 10 , into which a second piston 7 is guided . the first and second pistons 6 , 7 delimit the first transmission chamber 10 . the first piston 6 is in turn guided in a cylinder - shaped chamber of a housing , which has an end surface 15 on the face end to the first piston 1 . an aperture 16 is placed in the end surface 15 , through which a piston rod of the second piston 7 is guided . the piston rod has a smaller diameter than the second piston 7 . the piston rod passes via a ring - shaped recess in the wider diameter of the second piston 7 . a second transmission chamber 11 is configured between the end surface 5 , the recess and a ring - shaped face surface 17 of the first piston 6 . the second transmission chamber 11 is hydraulically connected to the first transmission chamber 10 via a first sealing gap 18 , which is configured between a side wall of the second piston 7 and inner wall of the first piston 6 . the first transmission chamber 10 is delimited by a second end surface 19 of the first piston 6 and a second face surface 20 of the second piston 7 . the first sealing gap 18 is designed in a narrow manner so that transient pressure differences are not compensated . furthermore , the second transmission chamber 11 is connected to a compensation chamber 22 via a second sealing gap 21 , which is configured between the outer wall of the first piston 6 and the inner wall of the housing 4 . the first transmission chamber 10 is hydraulically connected to the compensation chamber 22 via a bore 60 , which is placed in the first piston 6 . the first piston 6 passes into the piston rod 51 via a second recess . the piston rod 51 is essentially in the form of a cylinder and has a smaller diameter than the first piston 6 . in a first embodiment according to fig5 , an elastomer ring is placed between the housing and the second piston 7 and / or the piston rod 51 of the first piston 6 . the elastomer ring 50 is thereby connected in a circumferentially sealed manner to the housing 5 on the outside and to the piston rod 51 on the inside . a vulcanization method is used to effect the connection . the housing 5 and the first piston 6 having piston rod 51 are made of steel . the geometry of the elastomer ring is such that the elastomer ring has sufficient elasticity and at the same time the necessary stability to delimit the pressure of the compensation chamber 22 . due to its elastic properties , the elastomer ring should enable the volume in the compensation chamber to grow and also prevent too high an increase in pressure . the first and second transmission chambers 10 , 11 and the compensation chamber are filled with a transmission fluid . in this way , it is possible to achieve a motive link between the first and second pistons 6 , 7 . if the first piston 6 is moved deeper into the housing 5 by the actuator , the second piston 7 is in turn moved deeper into the housing 5 . inverse motion is thus achieved between the first and second pistons 6 , 7 . the compensation chamber 22 is connected to the second transmission chamber 11 via the second sealing gap 21 , the second sealing gap 21 being designed in such a narrow manner that transient pressure differences between the transmission chamber 11 and the compensation chamber 22 are not compensated . the term transient is understood to mean activating times of the actuator that the actuator requires in order to activate a setting element , in the example shown to activate the injection needle . pressure differences lasting for a longer period of time are compensated via the second sealing gap 21 between the second transmission chamber and the compensation chamber 22 . in this way , it is possible to automatically achieve a compensation of clearance . the first and second pistons 6 , 7 can therefore always be laid onto an actuator and / or a setting element . the transmission element is preferably under pressure . the pressure can for example be transmitted to the transmission fluid via the elastomer ring 50 using a tension device . instead of the embodiment shown in fig2 , it is also possible to select other arrangements of the transmission chambers , so that a movement of the first piston 6 is transmitted in order to effect a movement of the second piston 7 in the same direction . in a preferred embodiment according to fig2 , the elastomer ring 50 is connected to a first outer sleeve 52 on the outside and to a second inner sleeve 53 on the inside . the first sleeve 52 is connected in a circumferentially sealed manner to the housing 5 , preferably welded . the connection surface can be arranged on the inside or on a face end of the housing . on the inside surface , the second sleeve 53 is connected in a circumferentially sealed manner to the piston rod 51 , preferably welded . using an outer and inner sleeve 52 , 53 has the advantage of making it possible to carry out the connection process between the elastomer ring 50 and the outer and inner sleeve 52 , 53 independently of the connection process between the outer and inner sleeve 52 , 53 and the housing 5 and / or piston rod 51 . in a preferred embodiment , a tension device is provided , which is used to pretension the elastomer ring 50 in the direction of the compensation chamber 22 . in a simple embodiment , a spiral spring 54 is provided for this purpose , which is clamped between a stop ring 55 and the elastomer ring 50 . the stop ring 55 is connected firmly to the piston rod 51 . in a preferred embodiment , a pressure transmission device is provided between the tension device and the elastomer ring 50 , said pressure transmission device transmitting the pretension force of the spiral spring 54 having a larger surface to the surface of the elastomer ring 50 . the pressure transmission device is preferably configured in the form of a pressure ring 56 . the pressure ring 56 preferably has a support surface essentially corresponding to the surface of the elastomer ring 50 . in a further preferred embodiment , the pressure ring 56 has a graduated guide , the pressure ring 56 being guided by the piston rod 51 in the area of the guide with the smaller diameter . in this way , the pressure ring 56 is guided axially , so that the pressure ring 56 is not able to tilt . in this way it is possible to ensure that the pressure ring 56 evenly transmits the pretension force preset by the spiral spring 54 onto the elastomer ring 50 via the lay - on surface of the pressure ring 56 . fig3 shows a schematic representation of the elastomer ring 50 . fig4 presents a view of the pressure ring 56 from below , clearly showing a contact surface 58 , which is used to support the pressure ring 56 on the elastomer ring 50 . the guide aperture 59 is also shown , through which the piston rod 51 is guided in a finally constructed state and via which the pressure ring 56 is guided in such a manner that it can move axially in the axial direction of the piston rod 51 . in this way it is possible to avoid tilting the support surface of the pressure ring 56 . in a preferred embodiment , a protective film 57 is affixed to the surface of the pressure ring 56 , which is assigned to that of the elastomer ring 50 . the protective film 57 is comprised for example of rubber and serves to protect the elastomer ring 50 from abrasion due to the pressure ring 56 . the protective film 57 preferably has a greater hardness than the elastomer ring 50 .