DE19959300A1 - Engine has lubricant ejection devices of constant capacity and frequency of ejection processes is varied to vary quantity of lubricant delivered to cylinder surface - Google Patents

Abstract

The engine has at least one cylinder with a reciprocally movable piston and several outlets for delivering lubricant to the cylinder surface. Each outlet of a common rail associated with at least one group of outlets is associated with a constant capacity ejection device supplied with lubricant with an associated controllable actuator. The frequency of ejection is varied to vary the quantity of lubricant delivered to the cylinder surface. The engine has at least one cylinder (1) containing a reciprocally movable piston (6) and several lubricant outlets (17) for delivering lubricant to the cylinder surface. Each outlet of a common rail (14) associated with at least one group of outlets, and in which the lubricant is under a predetermined pressure, is associated with an ejection device (19) supplied with lubricant, which has an associated controllable actuator (20). The capacity of each ejection device is constant and the frequency of the ejection processes is varied to vary the quantity of lubricant delivered to the cylinder surface.

Description

The invention relates to an engine, in particular a two-stroke Large diesel engines with at least one cylinder and one arranged piston which along a tread of the Cylinder can be moved back and forth, preferably several Lubricant outlets arranged on the cylinder side for the supply of Lubricants are associated with each lubricant outlet one by means of at least one group of Lubricant outlets assigned to common rail, in which the Lubricant is present under a predetermined pressure with Lubricant supply device is assigned to the a controllable by means of a control device Actuator is assigned.

An arrangement of this type is known from EP 678 152 B1. In this known arrangement, the ejection devices trained as dosing pumps, the capacity of Dependence on a corresponding signal from the  Control device is changeable. The dosing pumps are actuated in time with the engine with each piston stroke. The the The amount of lubricant supplied to the tread can only be achieved by a change in the capacity of the metering pumps be changed. The known arrangement results in the Use of metering pumps to a comparative voluminous design. It can therefore be comparative large distances between the metering pump and the tread side Lubricant outlet result in a high System elasticity results from the errors in the actual Start of lubrication or at the actual feed Lubricant quantity can arise. In addition, the known arrangement the pro at every cycle of the engine Quantity of lubricant supplied as a result of the high frequency of the lubrication processes inevitably comparatively small, which affects the distribution of the Lubricant affects the entire tread.

Based on this, it is therefore the task of the present one Invention, an engine of the type mentioned with simple and to improve cost-effective means so that a reliable Lubrication guaranteed with economical lubricant consumption is.

This object is achieved in that the Capacity of each ejector is constant and that change the feed to the tread  Lubricant amount by means of the control device the frequency the ejection processes of the ejection devices can be changed.

The lubricant supplied to the tread becomes tight here controlled solely by the frequency of the ejection processes. A variable capacity of the ejection devices is therefore advantageously not required. this makes possible a simple and compact structure of the Ejection devices. These can therefore be advantageous close to the respective assigned lubricant outlet be placed, which is advantageous on the achievable accuracy affects. Another advantage of the invention Measures can be seen in the fact that not necessarily everyone Cycle of the engine an ejection process must be performed but the distances between successive ones Ejection processes can be selected as required. The Ejection devices can therefore have a comparatively large, have constant capacity, so that with each ejection process actually performed a comparative large amount of lubricant is ejected, which is favorable on affects the achievement of a good lubricant distribution and at the same time leads to a certain Faults caused by system elasticity hardly affect. Despite of the large capacity of the ejection devices is in Follow the frequency adjustment an economical Guaranteed lubricant consumption. The invention Measures allow the frequency of the Ejection processes of the various lubricant outlets  assigned ejection devices can be different. This ensures that the intensity of the Lubricate local needs within the tread Can be taken into account, d. H. for areas with high Lubricant requirements can provide high exhaust frequencies and vice versa, which is a particularly economical Guaranteed lubricant consumption.

Advantageous refinements and practical training of overriding measures are in the subclaims specified. So the control device can at least one Have input for a load-dependent signal and on hand this signal is the frequency of the ejection processes of the Determine ejection devices. This results in an advantageous manner a particularly reliable lubrication since the Lubricant requirement is very heavily dependent on the load.

The control device can expediently also have at least one Input for an actual value of one of the supplied Lubricant quantity dependent parameter, preferably for the Lubricant temperature, and if there are deviations in the Actual value from a predetermined target value is the frequency of the Change ejection processes accordingly. This measure results a closed loop, which is a particularly high Security guaranteed.

The control device can also advantageously have an input for a have signal dependent on the engine cycle and the frequency of the  Ejecting operations of the ejectors in the engine stroke change corresponding levels. This ensures that the discharge of the lubricant always in the same position of the Piston takes place, which makes the lubrication highly effective guaranteed. The lubricant is expediently expelled during the upward stroke of the piston when passing by of the piston ring assembly at the lubricant outlet that is acted on.

The common rail with branches can be advantageous for everyone Ejection devices and / or associated with them Actuators may be provided. This will ensures that only one, across all cylinders common rail is required, which is a particularly simple structure guaranteed.

The control device can also expediently have outputs for all actuation devices must be provided. This will ensured that the actuators or groups are actuated differently by actuators can, which results in locally different lubrication Needs can be taken into account so that on the one hand reliable lubrication is guaranteed and on the other hand particularly economical lubricant consumption is achieved.

Each actuator is expediently a means of Control device assigned controllable switching element. there can be associated with a fluid line electromagnetically actuated switching valves or one  Activate circuit breaker assigned to the power line. Elements of this type are comparatively robust and possess short response times, which is beneficial to security and Accuracy affects.

Since the capacity of the invention Ejection devices is constant, it is advantageous also possible that of a group of lubricant outlets assigned ejectors a common Assign actuator. This makes one special simple and compact structure and particularly facilitates also the wiring with the control device.

Further advantageous configurations and expedient Further training of the overarching measures are in the remaining subclaims specified and from the Example description below using the drawing removable.

In the drawing described below:

Fig. 1 is a schematic representation of a two-stroke large diesel engine with an inventive lubricating device can be acted upon by the lubricant actuator,

Fig. 2 shows a variant of Fig. 1 with pneumatically actuable actuating device,

Fig. 3 shows a further variant of FIG. 1 with electromagnetically actuable actuator,

Fig. 4 shows a variant of Fig. 1 with only one lubricant connection for the actuating and ejecting device and

Fig. 5 shows an embodiment with a plurality of ejectors common actuating device in section.

The main field of application of the present invention is large engines, such as ship drives etc. Two-stroke large diesel engines of the type indicated in FIG. 1 are used. Engines of this type have a plurality of cylinders 1 arranged in series, which are accommodated on an engine frame 2 . The cylinders 1 are provided with inlet slots 3 in their lower region. In the example shown, the cylinders are provided with an outlet opening 4 arranged in the cylinder head and controlled by a valve. The cylinders 1 contain a combustion chamber 5 which is delimited by a piston 6 arranged in the cylinder 1 so as to be movable up and down. This is connected via a piston rod 7 to an axially parallel crosshead 8 , which interacts via a connecting rod 9 with a crankshaft 10 mounted in the engine frame 2 . The piston 6 is provided with circumferential piston ring grooves 11 , in each of which a piston ring 12 is arranged. The piston rings 12 arranged one above the other form a so-called piston ring package.

The inside of the cylinder 1 is designed as a running surface 13 with which the peripheral surfaces of the piston rings 12 cooperate. In order to ensure a long service life of the tread 13 and the piston rings 12 , the tread 13 is lubricated with a suitable lubricant. The lubrication device provided for this purpose contains a common rail 14 which runs through all cylinders 1 and in which the required lubricant is present under a predetermined pressure. For this purpose, the common rail 14 is assigned a pump station 15 , which is connected on the suction side to a lubricant container 16 . The pumping station 15 can expediently have two pumps, one of which functions as a so-called stand-by pump, which jumps in in the event of a fault in the first pump.

The lubrication device also has lubricant outlets 17 provided in the area of the cylinders 1 , indicated in the example shown by radial bores. Several lubricant outlets 17 are provided over the cylinder circumference and over the cylinder length. In the example shown, two rims arranged one above the other, each having a plurality of lubricant outlets 17 which are distributed uniformly over the circumference of the cylinder, are provided. These are positioned so that they pass through the above-mentioned piston ring package in the upper cylinder area.

The lubricant outlets 17 are each supplied with lubricant provided by the common rail 14 by means of a lubricant supply device 18 indicated by a dash-dotted outline in FIG. 1. In the example shown, the lubricant supply device 18 contains an ejection device 19 and an actuating device 20 assigned to it.

The ejection device 19 is formed here by a pin-shaped ejection piston which interacts with an associated supply cylinder which is connected on the pressure side to the associated lubricant outlet 7 . In the example shown, this connection is indicated by a line to simplify the illustration. In practice, however, the ejection device 19 can be attached to the associated lubricant outlet 17 without an intermediate line. In order to avoid a breakdown of the combustion gases into the lubricant supply device 18 , check valves 21 can be provided in the area of the lubricant outlets 17 . These can each be integrated in the lubricant supply device 18 , as indicated by the outline in the example shown.

An assigned ejection device 19 is expediently provided for each lubricant outlet 17 . In the example on which FIG. 1 is based, an actuating device 20 should be assigned to each ejection device 19 . This is designed here as a cylinder-piston unit, wherein the piston of the actuating device 20 can be connected to the piston of the ejection device 19 , so that a one-piece double-piston arrangement results. The piston of the actuating device 20 has a larger diameter than the piston of the ejection device 19 , as a result of which a high ejection force can be achieved with a low operating pressure. Of course, it would also be conceivable to assign a common actuating device to several ejection devices. Such an embodiment will be explained in more detail below in connection with FIG. 5.

The common rail 14 is provided with stub lines 22 leading to the individual ejection devices 19 . A spur line 22 is assigned to each ejection device 19 and thus to each lubricant outlet 17 . The stub lines are arranged in such a way that the cylinder of the assigned ejection device 19 is filled with lubricant which is present in the common rail 14 under the desired pressure when the ejection piston is retracted into an initial position. In the example shown, a check valve 23 is provided at the end of the spur lines 22 on the ejection device side, which is set such that it can be overcome by the pressure present in the common rail 14. The check valve 23 ensures that a separation between the ejection device 19 and the common rail 14 is ensured during the ejection process.

The capacity of the ejection device 19 is constant, ie the above-mentioned starting position of the ejection piston cannot be changed. In the example shown, this is illustrated by a fixed stop 24 , on which the double piston arrangement mentioned above starts in the retracted position. The return movement of the double piston arrangement mentioned is brought about by a return spring 25 .

To carry out a discharge operation, ie for ejecting the quantity of lubricant contained in the supply cylinder of the ejector 19, the ejector piston of the ejector 19 is retracted by means of the associated actuator 20 into the associated storage cylinder of the ejector 19th For this purpose, the piston of the cylinder-piston assembly forming the actuating device 20 is acted upon by a pressure medium on the side facing away from the ejection piston.

In the example shown, the lubricant present in the common rail 14 under a certain pressure is used for this. For this purpose, the common rail 14 with leading to the actuators 20, in Fig. 1, indicated by a broken line branch pipes 26 is provided. Since the piston of the actuating device 20 has a larger diameter than the associated ejection piston, a sufficient ejection force is obtained in front of and behind the aforementioned double piston arrangement despite the same liquid pressures. A switching valve 27 is arranged in the branch lines 26 and can be controlled by means of a control device 28 . The switching valve 27 can be an electromagnetically actuated slide valve which has two switching packages, namely open and closed.

Of course, it is conceivable, in deviation from the example on which FIG. 1 is based, not to use the lubricant present in the common rail to drive the actuating device, but to use a different pressure medium, for example hydraulic oil or compressed air. An arrangement of this type with pneumatically drivable actuator 20 a is FIG. 2 as a basis. In Fig. 2, a compressed air source 30 is indicated, from which a compressed air line 26 a leads, which leads to a pressure medium supply device 18 a associated with a pressure medium outlet, not shown, the structure and arrangement of which may correspond to the example on which FIG. 1 is based. The compressed air line 26 a accordingly leads via a switching valve 27 a, which can be controlled by means of a control device of the type indicated in FIG. 1, as indicated by the signal line 29 a. The switching valve 27 a can in turn be an electromagnetically actuated slide valve.

Fig. 3 shows an alternative with an electromagnetically driven actuator 20 b. The FIG. 3 underlying lubricant delivery contains b 18, b 19, and an actuating device 20 b as in the previously described examples, an ejector. The structure and operation of the ejection device 19 b corresponds to the examples above. The actuating device 20 b is provided instead of a piston with a magnet armature 31 connected to the ejection piston of the ejection device 19 b, to which a magnet coil 32 is assigned. The armature 31 is slidably guided in the axial direction, which is indicated in the example shown by a cylindrical housing which is encompassed by the coil 32 . This is connected to a power source 34 via power lines 33 . In line 33 there is a switching element in the form of an interrupter switch 27 b, which can be controlled by an associated control device of the type indicated in FIG. 1, as indicated by signal line 29 b.

Again, the Fig. 4 shows an embodiment with operable by the extracted from the common rail 14c lubricant lubricant supply 18 c. This includes a one part, with the associated lubricant outlet 17 and on the other hand with a branch off from the common rail 14c supply line 26 c connected unit 35, which acts as the ejection means and actuating means. The actuating device 20 c is designed such that the associated ejection device 19 c can be supplied with lubricant through it. It is therefore sufficient c only one branching off from the common rail 14c supply line 26 in which a switching valve 27 is disposed c which is controllable by a control device the direction indicated in Fig. 1 type as indicated c through the signal line 29. The function is such that, after carrying out a discharge operation takes place automatically a filling of the discharge means with simultaneous return of the actuator to the original position, so that c at the next operation of the switching valve 27 immediately discharging operation can take place.

In the example shown, the control device 28 is provided with outputs 36 for all assigned lubricant supply devices 18 or their switching elements 27 . Each output 36 is connected to the associated switching element 27 by a signal line 29 . This enables simultaneous data transmission. However, a sequential data transmission with a so-called data bus would also be conceivable, which has outputs for each lubricant supply device 18 or its switching elements 27 . A connection of several switching elements, for. B. all the at the same height of a cylinder and distributed over the cylinder circumference arranged lubricant supply devices 18 associated switching elements 27 , in the form of a loop would be conceivable, with each loop preferably being assigned a data bus output. As soon as the switching element 27 is activated in a suitable manner, an ejection process is initiated. Since the capacity of the ejection device is constant in any case, the tread 13 is supplied with a constant amount of lubricant at each ejection process via the relevant lubricant outlet 17 . In order nevertheless to be able to adapt the total quantity supplied to the special requirements, the control device 28 is designed such that the ejection frequency, ie the distance between successive ejection processes, can be changed. The total amount of lubricant supplied and, accordingly, the output frequency are expediently set as a function of the load acting on the engine. But the additional consideration of special operating conditions, such as reversing or braking, can also be advantageous.

The control device 28 accordingly has at least one input 37 for a load-dependent signal, for example the torque acting on the crankshaft 10 . This is recorded by means of a suitable sensor 38 , which is connected via a signal line 39 to the associated input 37 of the control device 38 . The controller 28 may determine the required lubricant etc. total amount and the ejection frequencies therefrom resulting from the applied at input 37, the load-dependent signal on hand in their filed curves and tables. Feedback is provided to increase security. For this purpose, the control device 28 is provided with a further input 40 for a signal which is dependent on the quantity of lubricant supplied. This can be a signal corresponding to the lubricant temperature. For this purpose, a suitable sensor 41 is provided, which is connected via a signal line 42 to the assigned input 40 of the control device 28 . The measured actual value of the lubricant temperature is compared with a target value or target value range stored in the control device 28 . In the event of deviations, the control device 28 changes the discharge frequency in the required direction until the lubricant temperature reaches the desired target value.

The output frequency is changed by the control device 28 within the engine cycle, that is to say in 6 steps corresponding to one stroke of the piston. The control device 28 is accordingly also provided with an input 43 for a signal which correlates with the engine cycle, for example the speed of the crankshaft 10 or the stroke of the piston 6 or crosshead 8 . In the example on which FIG. 1 is based, a sensor 44 assigned to the crosshead 8 is provided for recording such a signal and is connected via a signal line 45 to the assigned input 43 of the control device 28 . The timing of the control device 28 that can be achieved in this way ensures that the ejection processes always take place at the desired position of the piston 6 , even if a lubricant ejection is not carried out with each stroke of the piston 6 . The control is expediently carried out in such a way that the lubricant is ejected when the piston ring assembly passes the relevant lubricant outlet 17 during the upward stroke of the piston 6 .

The discharge frequency specified by the control device 28 can be the same for all pressure medium outlets 17 . Different frequencies are also conceivable. As a rule, it is expedient if the lubricant is ejected simultaneously at the lubricant outlets 17 which are distributed at the same height over the piston circumference, that is to say if the ejection frequency is the same in this regard. With regard to the lubricant outlets which are offset with respect to one another in the axial direction, a different discharge frequency can be provided. For example, the lubricant outlets 17 , which are located approximately in the upper reversal area of the piston 6 below the first piston ring 12, can be acted upon with lubricant under normal load conditions with every second piston stroke. The same applies to the lubricant outlets 17 located below the last piston ring. The lubricant outlets located in between can be acted upon less frequently, for example only every third stroke of the piston 6 , with lubricant.

The control device 28 can expediently have a main control device and an auxiliary control device which jumps in as soon as a malfunction of the main control device occurs. The main and auxiliary control devices are expediently designed as computers, which results in short reaction times. To program and / or to enable manual intervention in the control processes, the control device can be assigned a communication device which is provided with a display and a keyboard and is not shown here. Advantageously, the control device 28 can also have an output assigned to an alarm device (not shown), so that in the event of imminent danger, e.g. B. if the lubricant temperature rises too much, an alarm is triggered or the engine can be switched off.

In the examples on which FIGS. 1 to 4 are based, each ejection device is assigned its own actuating device. However, it would also be conceivable, as already indicated above, to assign a common actuating device to a group of ejection devices, for example the ejection devices associated with all the lubricant outlets 17 arranged at the same height. An arrangement of this type is based on FIG. 5.

The lubricant supply device 46 shown in FIG. 5 contains a block 47 with a number of bores 48 corresponding to the number of respectively assigned, not shown, lubricant outlets, which are each connected to the respectively assigned lubricant outlet via a line 50 provided with a check valve 49 . A pin-shaped ejection piston 51 is assigned to each bore 48 to form an ejection device. The block 47 is accommodated in a cylindrical housing 52 , the interior area 53 of which is adjacent to the block 47 can be acted upon with a lubricant present in the common rail under a certain pressure via a branch line 54 coming from a common rail (not shown here).

The block 47 is provided with a circumferential groove 55 which intersects the bores 48 . In the area of each bore 48 there is thus an inlet slot 56 through which lubricant can flow from the interior area 53 into the associated bore 48 of the block 47 . The bores 48 and the associated ejection piston 51 are expediently arranged on a partial circle coaxial with the axis of the block 47 .

The ejection pistons 51 cooperate at their rear end facing away from the block 47 with a common thrust plate 57 , which can be displaced against the force of a return spring 60 by means of a feed piston 59 arranged in an associated bore 58 of the housing 52 such that the ejection pistons 51 into the assigned holes 48 are retracted. The thrust plate 57 is designed as a flange of a piston rod 61 which projects from the feed piston 59 and which is guided with its front end in a central bore 62 of the block 47 which is coaxial with the bore 58 . The return spring 60 is supported on the one hand on the block 47 and on the other hand on a further flange 63 of the piston rod 61 which projects radially beyond the flange which forms the thrust plate 57 .

The feed piston 59 is displaceable by means of a pressure medium that can be introduced into the associated bore 58 . In the example shown, the lubricant present in the common rail under a certain pressure is again used as the pressure medium. For this purpose, a supply line 64 branching off the common rail is provided, which is connected to the bore 58 assigned to the feed piston 59 via a flow path formed by a bore system. A first slide valve 65 is located in this flow path. This can be displaced into its position releasing the associated flow path by means of a pressure medium against the force of a return spring. The lubricant provided by the common rail is also used as pressure medium. For this purpose, a flow path 66 , which branches off from the interior area 53 of the lubricant and is formed by a bore system, leads to the slide valve 65 and is controlled by a second slide valve 67 , which is designed as an electromagnetically actuated switching valve and by a control device shown in FIG. 1 28 indicated type is controllable, as indicated by the signal line 29 . In order to make the displacement caused by the feed piston 59 during the ejection process harmless, the interior of the housing 52 is connected to the common rail via a return line 68 .

Above are some exemplary embodiments of the invention explained in more detail without, however, a limitation should be connected. Rather, the skilled person has a number of options available to the general idea the solution according to the invention to the circumstances of the individual case adapt.

Claims (17)

1. Engine, in particular two-stroke large diesel engine, with at least one cylinder ( 1 ) and a piston ( 6 ) arranged therein, which can be moved back and forth along a running surface ( 13 ) of the cylinder ( 1 ), the multiple, preferably arranged on the cylinder side lubricant outlets (17) are associated to the supply of lubricant, each lubricant outlet (17), suppliable with lubricant by means of at least assigned to a group of lubricant outlets (17) common rail (14), in which the lubricant is present under a predetermined pressure ejector ( 19 ; 48 , 51 ), to which an actuating device ( 20 ; 57-59 ) controllable by means of a control device ( 28 ) is assigned, characterized in that the capacity of each ejection device ( 19 , 48 , 51 ) is constant and that for changing the quantity of lubricant supplied to the tread ( 13 ) by means of the control device ( 28 ) the frequency de r ejection processes of the ejection devices ( 19 ; 48 , 51 ) is changeable. 2. Motor according to claim 1, characterized in that the control device ( 28 ) has at least one input ( 37 ) for a load-dependent signal and uses this signal to determine the frequency of the ejection processes of the ejection devices ( 19 ; 48 , 51 ). 3. Motor according to one of the preceding claims, characterized in that the control device ( 28 ) has at least one input ( 40 ) for an actual value of a parameter dependent on the quantity of lubricant supplied, preferably the lubricant temperature, and in the event of deviations from the actual value of the frequency of the ejection processes of the ejection devices ( 19 ; 48 , 51 ) changes in accordance with a predetermined target value. 4. Motor according to one of the preceding claims, characterized in that the control device ( 28 ) has at least one input ( 43 ) for a signal dependent on the engine cycle and the frequency of the ejection processes of the ejection devices ( 19 ; 48 , 51 ) in stages corresponding to the engine cycle changes. 5. Motor according to one of the preceding claims, characterized in that the ejection devices ( 19 ; 48 , 51 ) are each activated so that the lubricant is ejected when the piston ( 6 ) is lifted upwards as the piston ring assembly passes the lubricant outlets ( 17 ). 6. Engine according to one of the preceding claims, characterized in that the ejection devices ( 19 ; 48 , 51 ) of lubricant outlets ( 17 ) arranged offset with respect to one another in the direction of the cylinder axis can be actuated with different frequencies. 7. Motor according to one of the preceding claims, characterized in that the common rail ( 14 ) is provided with branches ( 22 or 26 ) for all ejection devices ( 19 ; 48 , 51 ) and / or actuating devices ( 20 ; 57-59 ) . 8. Motor according to one of the preceding claims, characterized in that the control device ( 28 ) is provided with outputs ( 36 ) for all actuating devices ( 20 ; 57-59 ). 9. Engine according to one of the preceding claims, characterized in that a common actuating device ( 57 , 58 , 59 ) is assigned to the ejection devices ( 48 , 51 ) assigned to a group of lubricant outlets ( 17 ) of a cylinder ( 1 ) which are preferably arranged at the same level. 10. Motor according to one of the preceding claims, characterized in that each actuating device ( 20 ; 57-59 ) is assigned a switching element ( 27 ; 67 ) which can be controlled by means of the control device ( 28 ). 11. Motor according to claim 10, characterized in that the actuating device ( 20 ; 57-59 ) is designed as a cylinder-piston unit which can be actuated by means of a pressure medium which can be actuated by means of the switching element ( 27 ; 67 ) which can be controlled by the control device ( 28 ). is controllable up and down. 12. Motor according to claim 11, characterized in that the piston of the actuating device ( 20 ; 57-59 ) has a larger diameter than the piston of the associated ejection device or devices ( 19 ; 48 , 51 ). 13. Motor according to one of claims 11 or 12, characterized in that the actuating device ( 19 ; 57-59 ) with a hydraulic fluid, preferably with lubricant removed from the common rail ( 14 ), can be acted upon. 14. Motor according to claim 13, characterized in that for the ejection device ( 19 c) and the actuating device ( 20 c) associated therewith, a common supply line ( 26 c) containing a switching valve ( 27 c) which can be controlled by the control device ( 28 ) is provided that branches off from the common rail ( 14 c). 15. Motor according to claim 11 or 12, characterized in that the actuating device ( 20 a) with compressed gas, preferably compressed air, can be acted upon. 16. Motor according to one of the preceding claims 1 to 10, characterized in that the actuating device ( 20 b) has a magnet armature ( 31 ) to which a coil ( 32 ) which can be supplied with current is assigned, the coil ( 32 ) in the power supply an interrupter ( 27 c) which can be controlled by means of the control device ( 28 ) is arranged. 17. Motor according to one of the preceding claims, characterized in that the ejection device ( 20 ) is followed by a check valve ( 21 ) which forms a structural unit with the ejection device ( 20 ).