JP5676869B2 - Large diesel engine - Google Patents

Description

  The invention relates to a large diesel engine as described in the introduction of the independent claim 1.

  A large diesel engine can be designed as a two-cycle engine or a four-cycle engine, but also as a drive unit for ships or in stationary operation, for example driving a large generator for generating electrical energy Often used. In this respect, the engine is in principle operated in a permanent operation for a considerable period of time, which places high demands on operational safety and operability. Therefore, in particular, the long intervals between inspections, low wear and economical handling of fuel are important criteria for the operator.

  In this respect, cylinder lubrication and piston lubrication are of primary importance. In the operating state, the piston slides along the inner wall of the cylinder, which acts as a sliding surface and is usually made in the form of a cylinder liner. On the one hand, the piston needs to slide as easily as possible, i.e. without any obstacles in the cylinder, while on the other hand, the piston efficiently converts the energy released in the combustion process into mechanical work. Therefore, the combustion space in the cylinder must be sealed as tightly as possible.

  For this reason, lubricating oil is usually introduced into the cylinder during diesel engine operation in order to achieve excellent sliding characteristics of the piston and to keep cylinder wall, piston and piston ring wear as low as possible. Is done. The lubricating oil further functions to neutralize aggressive combustion products while at the same time avoiding corrosion. Due to these many requirements, very expensive and expensive materials are frequently used as lubricating oils.

  The lubrication system used in today's large diesel engines uses lubricant (usually lubricating oil) through the cylinder wall and piston sliding surface to distribute the lubricant to the sliding surface as the piston ring moves. Or directly into the piston ring package of the piston. The introduction of the lubricant takes place via a lubrication point, which generally forms a nozzle outlet opening, a lubrication bar or a so-called quill.

  Usually, one lubricating oil pump is used for one cylinder, and the individual lubricating points are supplied. The lubricant pump supplies lubricant to all lubrication points of the cylinder. Depending on the structural design, the oil pump may be several meters away from each cylinder or each lubrication point.

  It is a problem of the known system that it is not impossible to do exactly the desired injection, but it involves great difficulties.

  For example, if lubricant must be introduced into the piston ring package depending on the position of the lubrication point at the maximum engine speed, the feasible time is a few milliseconds for the piston ring package to pass the lubrication point There is only. For example, due to the inertia of the system caused by the compressibility of the lubricant or the inertia of the liquid, the lubricant pump needs to have a lead time for compensation. The lead time must be determined and set in a complex and / or expensive manner.

  Depending on wear in the system or depending on operating conditions, this required lead time will vary and must be monitored and compared to the effective introduction time and optionally corrected.

  Despite such measures, there is still the potential for inconveniently high inaccuracy with respect to the effective introduction time of the lubricant. This is because, for example, the distance between the lubrication point and the lubricant pump that supplies the same is substantially different, whereby the inertia of the liquid of the moving lubricant is different, resulting in a difference in compressibility.

  Therefore, starting from this prior art, the object of the present invention is to provide cylinder or piston lubrication that is as efficient and flexible as possible and that allows the introduction time of the lubricant to be set very accurately in a simple manner. It is to provide a large diesel engine with a lubrication system that enables it.

  The subject of the invention for this purpose is characterized by the structure of the independent claims.

  Accordingly, in accordance with the present invention, a large diesel engine having at least one cylinder, the cylinder having a bore and a longitudinal axis, wherein the piston is configured to reciprocate along a sliding surface within the cylinder. A lubrication system is provided for the lubrication of the cylinder, the lubrication system comprising at least two lubrication points and a lubricant supply so that the lubricant can be supplied to the sliding surface through the lubrication points A large diesel engine is provided wherein the lubricant supply is adapted to deliver lubricant from a lubricant reservoir to a lubrication point. The lubricant supply comprises at least one pump nozzle unit located at the lubrication point, so that each pump nozzle unit can supply lubricant to a maximum of two lubrication points. The unit includes a pump connected to at most two lubrication points.

  The pump nozzle unit is provided directly at the lubrication point, in particular the lubrication point forms an opening at the nozzle outlet, so that the distance between the pump and the lubrication point supplied thereby is It becomes very short. Thus, problems arising from long lines, particularly those based on lubricant liquid inertia and compressibility, are at least greatly mitigated and allow increased accuracy in terms of lubricant introduction time.

  The pump of each pump nozzle unit can be operated independently of the pump of another pump nozzle unit. Each independently operable pump is provided for one or up to two lubrication points, resulting in a very flexible and efficient cylinder lubrication, especially for each operating condition of large diesel engines Can be applied in various ways.

  In order to make the accuracy of lubricant introduction as accurate as possible in time, the distance between the pump discharge part of the pump / nozzle unit and each lubrication point connected to the discharge part is the maximum. And preferably the same size as the diameter of the bore of the cylinder.

  In a preferred embodiment, the pump nozzle unit includes at least one nozzle connecting the pump discharge to one of the lubrication points, each nozzle being at most as long as the diameter of the cylinder bore. .

  In the preferred embodiment, one pump nozzle unit is provided at each lubrication point, and preferably can be operated independently, so that each lubrication point can be controlled independently and with good time accuracy. . Thereby, a very high flexibility with respect to the lubrication of the cylinder can be realized.

  In a preferred embodiment, there is provided at least one pump nozzle unit connected to two lubrication points and configured such that the spacing between the pump discharge and lubrication point is equal for both lubrication points. Yes. An embodiment with two lubrication points per pump nozzle unit simplifies the device and / or reduces costs. Because the lubrication points are at the same distance from the pump nozzle unit, i.e. they are arranged symmetrically with respect to the pump nozzle unit in particular, the line lengths between the lubrication points and the pumps supplying them are different. All the problems that arise from this can be avoided.

  From the point of view of a very simple structure, the preferred embodiment is that the pumps of the pump nozzle unit are each made as a piston pump so that the operating piston can reciprocate in the pump space within the piston pump. It is configured, and a certain amount of lubricant is sent to the nozzle through the discharge part of the pump for each stroke.

  In a variant, the pump of the pump nozzle unit includes a plurality of operating pistons, each operating piston being configured in an individual pump space. The amount of lubricant transported to the lubrication point per operating cycle can be set, for example, by a simple method using this configuration. For example, in partial load operation, if the required amount of lubricant is small, only one operating piston can be operated, and if the required amount of lubricant is large, two or more operating pistons are operated. .

  For embodiments where the working nozzle of the pump nozzle unit and the associated pump space are configured to carry different amounts, the working piston of the pump nozzle unit is operated with a constant carrying capacity, so Particularly advantageous. When the required amount of lubricant is reduced, an operating piston with a lower transport amount per stroke can be operated, whereas when the required amount of lubricant is increased, the transport amount per stroke is reduced. Larger working pistons can be actuated and / or multiple working pistons can be actuated.

  It is preferable that the pump of the pump-nozzle unit can be operated by hydraulic pressure or pneumatic pressure, or by a combined hydraulic / pneumatic type.

  Naturally, it would be advantageous if the pump of the pump-nozzle unit could be operated electrically.

  In a preferred embodiment, the lubrication system includes a common rail reservoir for lubricant connected to all lubricant supplies.

  It is particularly advantageous in terms of efficient and flexible lubrication in the cylinder when the lubrication points are arranged at different positions with respect to the axial direction represented by the longitudinal axis of the cylinder. That is, the lubricant can be introduced into the cylinder at different levels.

  It is advantageous if at least two lubrication reservoirs for different lubricants are provided so that different lubricants can be supplied to the lubrication points. Since in principle more than two lubrication points are provided in a large diesel engine, at least two different lubricants can be introduced into the cylinder according to the embodiment of the lubrication system of the present invention. Thus, for example, in the vicinity of the combustion space, a particularly preferred lubricant for the neutralization of aggressive combustion products is introduced, and in a position further away from the combustion space, a lubricant with particularly favorable sliding properties is used. be able to. It is also possible to use different lubricants for cylinder lubrication depending on the operating state of the engine, eg partial load or full load.

  Further, it is preferable that a means for setting the amount of lubricant sent by the pump / nozzle unit to a presettable value is provided. Therefore, the cylinder can be lubricated in accordance with each operating condition.

  Further advantageous methods and preferred embodiments of the invention result from the dependent claims.

  The invention is explained in more detail below with reference to examples and drawings. It is shown schematically and is shown partially in cross-section rather than the full size.

1 is a schematic diagram of a first embodiment of a large diesel engine of the present invention. It is a schematic sectional drawing which passes along the cylinder of a 1st Example. It is a figure of the pump nozzle unit of 2nd Example of this invention large sized diesel engine. It is a figure of the modification regarding arrangement | positioning of a lubrication point. It is the schematic of the modification of a pump nozzle unit.

  FIG. 1 schematically shows a first embodiment of a large diesel engine of the present invention, which is indicated generally by the reference numeral 1 and can be designed as a two-cycle engine or a four-cycle engine. . FIG. 2 shows a schematic cross-sectional view of one of a plurality of cylinders 2 of the large diesel engine 1 of FIG. The cylinder 2 has a bore, the diameter of which is indicated by B and the longitudinal axis is indicated by A. The cross section of FIG. 2 is perpendicular to the longitudinal axis A of the cylinder 2.

  The piston 3 is configured to reciprocate in the cylinder 2 in a known manner, and moves along the sliding surface 21 on the inner wall of the cylinder 2 in the operating state of the large diesel engine 1. The sliding surface 21 is usually formed by a cylinder insert or liner. The upper end of the piston 3 in the figure serves as the boundary of the combustion space 4 in which the combustion process takes place, and the piston 3 has a plurality of piston rings, generally indicated as a piston ring package 31 as a whole.

  In order to achieve the excellent sliding characteristics of the piston 3 and keep the wear of the cylinder wall, the piston 3 and the piston ring package 31 as low as possible, during operation of the large diesel engine 1, the piston 3, piston ring It is necessary to supply the sliding surface 21 with a lubricant that lubricates the package 31 and the sliding surface, such as lubricating oil. The lubricant further functions to neutralize aggressive combustion products while at the same time avoiding corrosion such as sulfur corrosion.

  A lubrication system 5 is provided for cylinder lubrication or piston lubrication. The lubrication system 5 comprises a plurality of lubrication points 6 through which the lubricant is supplied to the sliding surface 21. In the first embodiment, a total of eight lubricating points 6 are provided and arranged along the peripheral edge of the cylinder 2 (see FIG. 2). The lubrication points 6 each form an opening at the outlet of the nozzle 71 through which the lubricant is introduced into the cylinder 2. Within the framework of the present application, “nozzle” means any device suitable for the introduction of a lubricant, which, for example, in the narrow sense, through which the lubricant is concentrated and sprayed as a jet or atomized. It may be a nozzle that is injected in the form of, or a lubricant flows or drips therethrough, eg a channel or stub, called a quill, or the lubricant is introduced into the cylinder 2 of the large diesel engine 1 All other devices known for use.

  A lubricant supply 8 is further provided to send the lubricant from the lubricant reservoir 10 to the lubrication point 6. In this embodiment, the lubricant reservoir 10 is made as a common rail reservoir or accumulator and contains the lubricant at a pressure sufficient to allow the lubricant to flow out of the reservoir or accumulator and reach the lubrication point 6. To do. Lubricant is generally provided from the common rail reservoir at a pressure of 1-20 bar. Alternatively, it is of course possible to pump the lubricant out of the storage container by means of a pump (not shown), or allow the lubricant to enter a deep tank lubricant reservoir where it can flow out by gravity. Of course it is also possible.

  In the present invention, the lubricant supply unit 8 includes at least one pump nozzle unit 7 integrated with the lubricant supply unit 8 at the lubrication point 6, and each pump nozzle unit 7 has a maximum of two lubrications. It includes a pump 72 connected to at most two lubrication points 6 so that it can be fed to point 6. In the first embodiment, each pump 72 can operate independently from the pumps of all other pump nozzle units 7.

  In the first embodiment shown in FIG. 2, for each lubrication point 6, one independently operable pump nozzle unit 7 is provided, and the number of pump nozzle units is the same as the number of lubrication points 6. Each of the pump nozzle units 7 is provided with one lubrication point 6.

  The pump nozzle unit 7 integrated with the lubricating oil supply unit 8 is arranged directly at the lubrication point 6, for example, on the outer wall of the cylinder 2. The interval between them is very short. There is no connection line between the pump 72 and the nozzle 71 because the opening at the outlet of the nozzle 71 forms the respective lubrication point 6 and the nozzle 71 forms the pump nozzle unit 7 together with the respective pump 72. Substantially shorter reaction times are obtained from this lubrication, thereby greatly increasing the accuracy of lubricant injection.

  The distance D (FIG. 2) between the discharge part of the pump 72 of the pump nozzle unit 7 and the lubrication point 6 connected to the pump 72 is at most as large as the diameter B of the bore 2 of the cylinder. It is preferable. Specifically, it is preferable that the length of the nozzle 71 of the pump nozzle unit 7 that connects the discharge portion of the pump 72 to the lubrication point 6 is the same as the bore diameter of the cylinder 2 at the maximum.

  A check valve 73 (not shown in FIG. 2) is provided in each nozzle 71 to prevent the backflow of lubricant from the lubrication point 6 to the pump 72.

  The pump 72 of the pump nozzle unit 7 is manufactured as a piston pump, and is arranged in the piston pump so that the operating piston 74 can reciprocate in the pump space 75. During each stroke of the operating piston 74, a certain amount of lubricant is sent into the nozzle 71 through the discharge part of the pump 72.

  In order to actuate the operating piston 74 of the pump 72, a switching member 9 is provided which is an electrically controlled 3 / 2-way control valve in the embodiment shown in FIG. In the first switching position, the switching member 9 connects the back side of the operating piston 74 to a working medium supplied to the pressure storage unit 11, for example, a hydraulic medium, compressed oil, or compressed air. In the second switching position (position shown in FIG. 1), the switching member 9 connects the back side of the working piston 74 to the outlet line 103 and through it from the back side of the working piston 74 of the pump 72 to the working medium. Can be discharged. The switching member 9 further includes an electromagnet 91 for moving the switching member 9 from the second switching position to the first switching position against the force of the spring 92.

  Control of the electromagnet 91 for the operation of the switching member 9 is performed by the adjustment unit 12 connected to the switching member 9 via a signal line 200 indicated by a dotted line.

  The adjustment unit 12 has an automatic adjustment input unit 13 and a manual adjustment input unit 14, which are connected to the adjustment unit 12 by signals (indicated by dotted arrows 201 and 202 in FIG. 1). The self-adjusting input 13 automatically receives an input signal containing information about the current operating state, such as engine speed or load, or other system parameters such as crankshaft position or location, preferably in real time. . For the injection of the lubricant into the sliding surface 21, the time to be controlled, optionally the amount, and the lubrication point 6 are determined with reference to these input signals. The parameters or initial values can be manually transmitted to the adjustment unit 12 via the manual adjustment input unit 14.

  The lubrication system 5 operates in the operating state as follows. When no lubricant is supplied to the sliding surface 21, the lubrication system 5 is in the state shown in FIG. The switching member 9 is in a switching position where the back side of the operating piston 74 is coupled to the working medium outlet line 103. A pump space 75 is connected to the lubricant reservoir 10 via a line 100. A check valve 76 is provided in the line 100 to prevent the lubricant from flowing back from the pump space 75 to the lubricant reservoir 10. The lubricant is stored in the lubricant reservoir 10 and is in an overpressure condition slightly below normal pressure, for example 0.2-1 bar, which is sufficient to open the check valve 76. However, it is not sufficient to open the check valve 73 of the nozzle 71. Accordingly, the pump space 75 is completely filled with the lubricant, and the operating piston 74 reaches the bottom dead center, that is, the left end in the figure. Optionally, it is also advantageous to further load the working piston 74 by a spring (not shown) and bias the working piston 74 to this illustrated position.

  In order to start the lubrication measure, the adjusting unit 12 outputs a control pulse via the signal line 200 so that the electromagnet brings the switching member to the other switching position. Next, the back side of the working piston 74 is connected to a pressure storage for the working medium. The working medium flows out from the pressure storage unit 11 to the back side of the working piston 74 via the connecting lines 102 and 101, and moves the working piston 74 to the right until reaching the bottom dead center, that is, the right end in the figure. Let The lubricant in the pump space 75 is pushed through the nozzle 71 by this movement of the operating piston 74 and moves to the sliding surface 21 in the cylinder 2 via the lubrication point 6.

  Next, the adjusting unit 12 switches the switching member 9 to return to the switching position shown in FIG. 1 supported by the spring 92, whereby the working medium is discharged from the back side of the operating piston 74 and enters the outlet line 103. Thereby, the operating piston 74 is moved again to the bottom dead center in the figure, and the pump space 75 is again filled with lubricant via the line 100.

  When the working medium is compressed air, the working medium can be easily blown out through the outlet line 103. If the working medium is compressed oil or hydraulic fluid, it can be led back through the outlet line 103 and then fed back to the pressure storage 11 made, for example, as a common rail storage.

  In addition to the operation of the pump 72 by the above-described hydraulic pressure or pneumatic pressure, a combined pneumatic / hydraulic pressure type operation can also be realized.

  Direct electrical actuation of the pump 72 is also possible, by electromagnetic forces generated by coils and / or by other electrically actuated transducers or pulsars, such as piezoelectric crystal actuated transducers or pulsars, etc. The operating piston 74 reciprocates.

  Since the lubricant moves from the pump 72 and enters the nozzle 71 directly and reaches the lubrication point 6, the reaction time is extremely short compared to known lubrication systems for large diesel engines. Since both the inertia of the liquid between the pump 72 and the lubrication point 6 and the compressibility of the lubricant virtually do not produce a delay effect, a very high accuracy is obtained with respect to the time to lubricate. Since the piston 3 moves at a high speed, it can be seen that the lubrication process or positioning of the lubrication point 6 can be performed from the viewpoint that the lubrication can be performed only for several milliseconds per operation cycle.

  Since each pump nozzle unit 7 can operate independently from each other pump nozzle unit 7, very flexible and efficient lubrication can be realized. Thus, for example, if the need for lubricant is reduced, not all eight lubrication points 6 shown in FIG. 2 are not used, but only four of the pump nozzle units 7, for example. It is possible to feed the lubricant to the sliding surface 21 through only four of the total eight lubrication points 6.

  Embodiments in which the switching member 9 operates a plurality of pumps 72 of different pump nozzle units 7 are possible. For example, it is possible to provide one switching member 9 for one cylinder 2 and operate all the pumps 72 of this cylinder 2. This method simplifies the apparatus and reduces costs.

  Each pump 72 of the pump / nozzle unit 7 can be operated so as to transport a certain volume of the pump / nozzle unit 7 to introduce the lubricant. That is, for each operation of the operating piston 74, the total capacity of the pump space 75 is sent into the nozzle 71.

  An embodiment in which transport is performed with stroke control is also possible. In this respect, the switching member 9 is controlled in time so that the operating piston 74 sends some of the lubricant in the pump space 75 to the nozzle 71. The back side of the working piston 74 is decompressed in accordance with this purpose before the working piston 74 reaches the rightmost position in FIG. As a result, the conveying process is completed, the operating piston 74 moves to the left in the drawing, and the lubricant flows from the lubricant reservoir 10 to the pump space 75 via the line 100.

  It is advantageous to provide sensors that can detect the respective position of the working piston 74 in a stroke-controlled transport. This position is transmitted to the adjustment unit 12.

  FIG. 3 is a diagram of the pump nozzle unit 7 of the second embodiment of the large diesel engine 1 of the present invention. Functionally the same or equivalent parts have the same reference numbers as in FIGS.

  1, 2 and all the explanations made in connection with the first embodiment also apply to the second embodiment in a similar or the same sense.

  In this embodiment, the pump nozzle unit 7 is connected to two lubrication points 6. In this respect, the pump nozzle unit 7 is preferably arranged so that the interval between the discharge part of the pump 72 and the lubrication point 6 is equal to both the lubrication points 6.

  The nozzle 71 is produced as a branch nozzle 71 and here is divided into two arms 71 a and 71 b each reaching the lubrication point 6. Since the nozzle 71 is designed symmetrically, a completely simultaneous supply is ensured at both lubrication points. When measured with respect to the arm 71a or the arm 71b, the length of the nozzle 71 is preferably the same as the diameter B of the bore of the cylinder 2 at the maximum.

  Of course, two nozzles that open to the pump space 75 of the pump 72 or the discharge part of the pump 72 and are respectively led to one of the two lubrication points 6 can be provided instead of the branch nozzle 71. is there.

  FIG. 4 shows a modification of the arrangement of the lubrication points 6 that can be applied to both the first embodiment and the second embodiment.

  In this variant, the lubrication points 6 ′ and 6 ″ are arranged at different positions with respect to the axial direction determined by the longitudinal axis A of the cylinder 2. The lubrication point 6 'is arranged on the lower side in the drawing. On the other hand, the lubricating point 6 ″ is arranged on the upper side in the drawing and closer to the combustion space 4.

  In particular, in this variant it is also possible to provide at least two lubricant reservoirs 10 for different lubricants so that different lubricants can be supplied to the lubrication points 6 ′ and 6 ″. Thus, for example, in the vicinity of the combustion space 4, a particularly preferred lubricant for the neutralization of the aggressive combustion products is introduced through the lubrication point 6 ″ and sliding further away from the combustion space 4. Lubricants with particularly favorable properties can be used. It is also possible to use different lubricants for cylinder lubrication depending on the operating state of the engine, eg partial load or full load.

  Unlike the drawing of FIG. 4, it is also possible to supply two lubrication points 6 ′, 6 ″ arranged at different axial levels by the same pump nozzle unit 7, ie in a manner similar to FIG. it can.

  FIG. 5 shows a schematic diagram of a variation of the pump nozzle unit 7 applicable to both the first and second embodiments.

  In this variant, the pump nozzle unit 7 includes a plurality of operating pistons. That is, here, three working pistons 741, 742, and 743 are included, each disposed in an individual pump space 751, 752, and 753. In order to operate the respective working pistons 741, 742 and 743, switching members 9 ′, 9 ″ and 9 ′ ″ are provided, one for each working piston, in a manner similar to that described above. . This modification shows means for setting the amount of lubricant sent by the pump / nozzle unit 7 to a presettable value in addition to the above-described transport method by stroke control. That is, in this means, only one of the working pistons 741, 742, and 743 is actuated, or two, or all three are actuated per lubrication process.

  The pump spaces 751, 752, and 753 can be the same volume or different volumes. In the embodiment shown in FIG. 5, pump space 751 has the smallest volume, pump space 752 has the second largest volume, and pump space 753 has the largest volume. Therefore, if the operating pistons 741, 742, and 743 carry a certain amount so as to completely empty the pump spaces 751, 752, and 753, respectively, when only the operating piston 741 is operated, The transport amount is the smallest. When only one of the operating pistons 741, 742, 743 is operated, the conveyance amount is maximized when the operating piston 743 is operated.

  Of course, it is also possible to actuate two or all three of the working pistons 741, 742, 743 together. It is also possible to adapt the respective amount of lubricant conveyed in a simple manner, ideally to the respective operating state of the large diesel engine 1.

  It will be understood that the variant shown in FIG. 5 can also be operated by stroke controlled transport.

  Unlike the embodiment shown here, it is also possible to provide a lubrication point on the piston 3 of the large diesel engine 1 so that lubricant is supplied from the piston 3 to the sliding surface 21. In this case, the pump nozzle unit 7 is also preferably arranged in the piston 3 or in the piston rod. An embodiment in which the lubrication point 6 is provided in both the piston 3 and the cylinder 2 is naturally possible.

DESCRIPTION OF SYMBOLS 1 Large diesel engine 2 Cylinder 3 Piston 4 Combustion space 5 Lubrication system 6 Lubrication point 6 'Lubrication point 6 "Lubrication point 7 Pump nozzle unit 8 Lubricant supply part 9 Switching member 9' Switching member 9" Switching member 9 '''Switching member 10 Lubricant storage unit 11 Pressure storage unit 12 Adjustment unit 13 Automatic adjustment input unit 14 Manual adjustment input unit 20 Signal line 21 Sliding surface 31 Piston ring package 71 Nozzle 71a Arm 71b Arm 72 Pump 73 Reverse Stop valve 74 Operating piston 75 Pump space 76 Check valve 91 Electromagnet 92 Spring 100 Line 101 Line 102 Line 103 Line 200 Signal line 201 Dotted arrow 202 Dotted arrow 741 Operating piston 742 Operating piston 743 Operating piston 751 Pump space 752 Pump During 753 pump space A longitudinal axis B bore D spacing

Claims (15)

A large diesel engine having at least one cylinder (2), said cylinder (2) having a bore (B) and a longitudinal axis (A), inside said cylinder (2), a piston (3) Is configured to be capable of reciprocating along the sliding surface (21), and a lubrication system (5) is provided for lubrication of the cylinder, the lubrication system comprising at least two lubrication points (6) and lubrication And a lubricant supply part (8), through which the lubricant can be supplied to the sliding surface (21) through the lubrication point (6), the lubricant supply part (8) being lubricated In a large diesel engine adapted to send lubricant from the agent reservoir (10) to the lubrication point (6),
The lubricant supply section (8) comprises at least one pump nozzle unit (7) arranged at the lubrication point (6), each pump nozzle unit (7) having a maximum of two of the lubrication so that it can supply a lubricant to the point (6), viewed including the pump each pump-nozzle unit (7) is coupled to two of the lubrication points at maximum (6) (72),
Each pump nozzle unit (7) includes at least one nozzle (71) connecting the discharge of the pump (72) to one of the lubrication points (6), and each nozzle (71) Is the same length as the diameter (B) of the bore of the cylinder (2), and there is no connecting line between the pump (72) and the nozzle (71). ·engine.   2. The pump (72) of each pump nozzle unit (7) can be operated independently of the pump (72) of another pump nozzle unit (7). Large diesel engine described in 1.   Any distance (D) between the discharge part of the pump (72) of the pump / nozzle unit (7) and each lubrication point (6) connected to the discharge part is a maximum of the cylinder (2). The large diesel engine according to claim 1 or 2, which has the same size as the diameter (B) of the bore.   Each pump nozzle unit (7) includes at least one nozzle (71) connecting the discharge portion of the pump (72) to one of the lubrication points (6), and each nozzle (71 A large diesel engine according to any one of claims 1 to 3, wherein) is at most as long as the diameter (B) of the bore of the cylinder (2).   5. A pump nozzle unit (7), one at each lubrication point (6), preferably enabled to operate independently. Large diesel engine as described in section.   Connected to the two lubrication points (6), and configured such that the interval between the discharge part of the pump (72) and the lubrication point (6) is equal for both the lubrication points (6), A large diesel engine according to any one of claims 1 to 4, wherein at least one pump nozzle unit (7) is provided.   The pumps (72) of the pump nozzle unit (7) are each made as a piston pump so that the operating piston (74) can reciprocate in the pump space (75) within the piston pump. 7. A composition according to any one of claims 1 to 6, wherein a configured amount of lubricant is sent to the nozzle (71) through the discharge part of the pump (72) for each stroke. Large diesel engine.   The pump (72) of the pump nozzle unit (7) includes a plurality of operating pistons (741, 742, 743), each operating piston being configured in an individual pump space (751, 752, 753). A large diesel engine as claimed in claim 7.   9. The working piston (741, 742, 743) of the pump nozzle unit (7) and the associated pump space (751, 752, 753) are designed to carry different amounts. Large diesel engine described in 1.   10. The pump (72) of the pump nozzle unit (7) can be operated by hydraulic or pneumatic pressure or by a combined hydraulic / pneumatic type. A large diesel engine as described in any one of the above.   11. The large diesel diesel engine according to claim 1, wherein the pump (72) of the pump nozzle unit (7) can be electrically operated. engine.   12. The lubricant system (5) according to any one of the preceding claims, wherein the lubrication system (5) comprises a common rail reservoir (10) for lubricant connected to all the lubricant supplies (8). Large diesel engine as described in section.   The lubrication points (6, 6 ', 6' ') are arranged at different positions with respect to the axial direction represented by the longitudinal axis (A) of the cylinder (2). Item 13. A large diesel engine according to any one of Items 12 to 12.   14. At least two lubrication reservoirs for different lubricants are provided so that different lubricants can be supplied to the lubrication points (6, 6 ′, 6 ″). A large diesel engine as described in any one of the above.   15. A means according to any one of the preceding claims, wherein means are provided for setting the amount of lubricant delivered by the pump nozzle unit (7) to a presettable value. Large diesel engine.

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