JP2018066383A - System and method for putting cylinder lubrication oil into large cylinder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a lubrication system, and a method for putting lubrication oil.SOLUTION: In a system and a method for putting cylinder lubrication oil into a large diesel engine cylinder, the system includes: a lubrication oil supply source that can be constituted by a pump station and an accumulator; a supply line from the lubrication oil supply source; some injectors having an inlet for injecting the cylinder lubrication oil to the coupled cylinder, an on-off valve part, and one or more nozzle ports being connected to the supply line, and corresponding to the number of engines or the number of the plural engine cylinders; and a control part for controlling each on-off valve part. Furthermore, the injector is used for a putting system. To overcome disadvantage depending on a flow rate and viscosity in the supply line, the system includes a flow rate measuring part per injector and/or cylinder, and the flow rate measuring part is connected to the control part used for adjusting closure of a passage.SELECTED DRAWING: Figure 1

Description

The present invention is a charging system for cylinder lubricant into a large diesel engine cylinder, for example a marine engine,
A lubricant supply that may be constituted by a pump station or an accumulator;
A supply line from a lubricant supply source;
Several inlets for injecting cylinder lubricant into connected cylinders, open / close valve sections, and one or more nozzle ports, connected to the supply line and corresponding to the number of cylinders of the engine or engines An injector,
The present invention relates to a charging system including a control unit that controls each on-off valve unit.

The present invention is further a method for injecting cylinder lubricant into a large diesel engine cylinder, such as a marine engine,
Pressurizing lubricating oil in a lubricating oil source, which may be constituted by a pump station or accumulator;
Directing the lubricating oil from the lubricating oil source through the supply line;
Injecting lubricant through several injectors having an injector connected to the supply line and having an inlet into a coupled cylinder, an on-off valve, and one or more nozzle ports;
And controlling each on-off valve unit by a control unit.

Furthermore, an injector used in a charging system for a cylinder lubricant into a large diesel engine cylinder, for example a marine engine,
A lubricant supply that may be constituted by a pump station or an accumulator;
A supply line from a lubricant supply source;
A number of injectors each having an inlet for connection to a supply line, an on-off valve portion, and one or more nozzle ports for injecting cylinder lubricant into a connected cylinder;
The present invention relates to an injector including a control unit that controls each on-off valve unit.

  The present invention is primarily intended for use in electromagnetically controlled injectors where the input is controlled by the valve opening time. This is different from other lubrication systems where the input is controlled primarily volumetrically. This amount of oil can have a mist shape, for example, by direct spray control since the valve has a built-in pump. In system operation, it will be performed primarily by valves that can be controlled by electromagnets.

  Today, there are mechanical, hydraulic and electromechanical cylinder lubrication systems.

  Today, prior art solutions based on time-controlled feeding have the disadvantage that their amount is highly dependent on the flow rate and viscosity conditions in the oil supply line.

  An electromechanical injector is known (for example, refer to Patent Document 1). A flow rate detector that integrates the switch function and emits a signal when there is a flow is used. The flow rate is monitored by a flow rate detector, and the duration of the flow rate is compared with a manually determined limit value. These are not flow measurement, but simply start and stop control of the flow signal.

  An injector and cylinder lubrication system is known (for example, refer to Patent Document 2). This technique is based on a system with an electromagnetic valve for each cylinder, which opens and closes for flow to the individual valves. This design has the disadvantage of imposing great demands on the same flow and viscosity conditions in the oil supply line to avoid different amounts of oil being delivered to each of the valves. For example, the distance and temperature conditions in the oil supply line should be kept very constant in order to ensure uniform transport in all lubrication points. In practice, this is a big problem. This prior art has another drawback. During operation monitoring, a pressure sensor is used to monitor the supply pressure to all injectors. From the hands-on experience, control learned to recognize one or more failed valve patterns. This method places great demands on the empirical data used for injector monitoring and for the same reasons of uncertainty arising in this problem.

  Local injectors based on the use of needle valves in needle-like valve bodies and corresponding valve seats are also known (see, for example, Patent Document 2). Leakage occurs when the needle is tilted with respect to the sheet or not aligned along the sheet. Therefore, the needle should be guided so that the needle is not displaced radially relative to the valve seat. This is mainly achieved by having a fine tolerance and adaptability to the needle and by valve boring (needle guide) in which the needle is placed. There is a disadvantage with this design that the injector typically has a substantial length since the injector extends through a relatively thick cylinder wall and lining. The valve seat should be as close as possible to the nozzle mouth to reduce the dead volume that is moved / accelerated before the valve begins to carry oil. This means a relatively fine tolerance on the boring of the nozzle where the needle is located, and the needle has a considerable length to ensure that the needle is accurately centered in the seat. Should be. This fine tolerance and fit between the needle guide and the needle can get stuck in the very narrow gap that appears between the needle and the needle guide, so the valve is affected by piping and lubricant contamination. This means that a relatively great demand is placed on the purity of the oil supplied to the injector. This can cause the needle to be offset from the center relative to the seat, or to prevent needle movement. In both cases, the valve function is reduced. This means that great demands are placed on the purity of the oil supplied to the injector.

  Also, a system corresponding to the system and method described in the introduction part is known (see, for example, Patent Document 3). This patent document does not disclose that the charging system has a flow rate measuring unit. Therefore, this patent document does not disclose how the flow rate measuring unit is arranged with respect to the injector and / or the cylinder. Further, this patent document does not disclose how the flow rate measurement unit is connected to the control unit. Further, this patent document does not disclose how to adjust based on a signal received by the control unit.

  Further, a lubricating device for injecting lubricating oil into the air / fuel mixture in the intake air in order to mix the lubricating oil and the air / fuel mixture before being sucked into the motor is disclosed (see, for example, Patent Document 4). ). This patent document relates to a significantly different motor technology for small combustion engines. Therefore, this patent document does not disclose the injection of lubricating oil into the cylinder through the injector. In addition, this patent document discloses that the controller controls the amount of the lubricant based on the temperature of the sliding portion and the engine speed. However, in this patent document, the load / index signal is conveyed directly to the control unit in order to control the timing and injection of one or more nozzles of the plurality of nozzles that inject the lubricating oil into the air / fuel mixture. This is not disclosed. In addition, this patent document does not disclose the necessity of controlling the timing of lubricating oil injection according to a reference signal from the engine.

  Further, a system corresponding to the system disclosed in Patent Document 4 is disclosed (for example, see Patent Document 5). This patent document does not disclose an injector for injecting lubricating oil into a cylinder. This patent document relates to a significantly different motor technology for small combustion engines. This patent document discloses that lubricating oil is conveyed to an intake manifold in a vacuum system. Although this patent document discloses that a flow sensor is used to determine the amount of lubricant conveyed from a pump, a sensor that can determine the amount of lubricant entering a particular cylinder Is not disclosed.

In practice, in some cases, it may be difficult to ensure sufficient purity of the supplied lubricant, for example, during installation or replacement of the injector, or with respect to prolonged shutdown. In these cases, filtration in the supply to the injector corresponding to a typical gap width of 5-10 μm or less would be desirable. However, establishing such microfiltration seems difficult in practice. Typically, there will be a problem establishing a stable supply of lubricant when the filter is not clogged / blocked at frequent intervals. Generally, a central filter is used throughout the system because it is difficult to attach and maintain a local filter in each cylinder or injector. Typically, there is no problem with central filtration of oil sufficient to avoid blocking one or more nozzle ports within individual injectors. In some cases, fixtures / filters are used that are installed locally on individual injectors. However, these are difficult to check and difficult to clean and use. For a dosing system for cylinder lubricant, several electromechanical injectors are used that are mounted within the cylinder wall and convey the lubricant into the cylinder. For injectors, it is true that the injector is actuated by a needle valve, and the following is true.
The injector is located through a cylinder lining and possible cooling jacket that defines the distance from the outer contour to the inner cylinder diameter to be 80-200 mm. Thereby, a long needle will be required and the guided length of the needle is proportional to the length of the needle. It is necessary to guide close to the valve seat for sealing between the needle and the seat. Therefore, a relatively long needle guide is likely to contain a great risk that dirt and foreign matter may enter and damage the function of the valve.
The valve seat on the injector should be as close as possible to the injector nozzle port to minimize dead volume between the nozzle port and the valve seat.
Special requirements are made for the design and manufacture, so that the fit between the needle guide and the valve body / needle to ensure that the valve body / needle is precisely centered with respect to the valve seat It is necessary to have a relatively fine tolerance on the degree.

  In practice, when operating with a needle valve, it may be difficult to filter out particles in the lubricant due to the reduction to the typical gap opening used in needles (ie, 5-10 μm or less). Absent. Typically, a central filter is used throughout the system because it is difficult to install and maintain a local filter in the cylinder. There is typically no problem with filtering the oil locally or centrally with a filter that filters out particles larger than 0.01 mm. In practice, experience typically shows that only a central filter with a mesh width of 0.025 mm or more can be applied. Such filtration is sufficient to avoid clogging the nozzle mouths or groups of mouths within the individual injectors. In order to prevent oil from becoming contaminated from blockage / clogging in the gap between the needle and the needle guide, the large gap creates a needle valve that is unsuitable for use, so large gaps and new There is a need for different types of valve bodies and seats.

European Patent No. 0049603 European Patent No. 1426571 European Patent No. 1582706 Japanese Patent Laid-Open No. 02-271019 U.S. Pat.No. 4,913,108

  The object of the present invention is to show a lubrication system and a method for injecting lubricating oil in which the disadvantages of the prior art systems are avoided.

  Furthermore, the object of the present invention is to show a simple injector which contributes to avoid the disadvantages of the prior art systems and is robust / reliable and even in operation.

  In order to overcome the disadvantages depending on the flow rate and viscosity in the supply line, the system according to the present invention comprises a flow measuring unit for each injector and / or for each cylinder, and the flow measuring unit is closed-circuit-adjusted. Connected to the control unit used in the control unit, a plurality of signal cables control the load / index signal so as to control the timing and input amount of one or more injectors per cylinder according to the reference signal from the engine Each injector is made as a unit, and the open / close valve is an electromechanical valve built in the injector for supplying lubricating oil. The electromechanical on-off valve includes a spring-loaded valve stem.

  The method according to the invention sends the result of the flow measurement to the control unit by means of a local flow measurement for each injector and / or a central flow measurement of the cylinder of the actual oil input per injector, and is expected or planned. Control the load / index signal to control the timing and input of one or more injectors per cylinder according to the reference signal from the engine. The control unit sends a control signal to the opening and closing unit for conveying the oil directly to the unit and adjusting the timing and amount of oil to the required range, and injecting the lubricating oil to inject the lubricating oil, the opening and closing valve In order to move the valve stem, the lubricating oil is charged by operating the open / close valve in the form of an electromechanical valve built into the injector. Rukoto is a feature.

  In this connection, the period from the operation of the injector to the start of the flow signal can be used to adjust the injection timing of the system. In this way, a margin can be provided for possible changes in timing due to viscosity conditions (delay of lubricant and accelerated transport). Deviations in the viscosity situation are interesting because they determine temporal performance and can cause fast or slow timing for injection.

  The injector is characterized in that the opening / closing valve includes a ball valve body and an interacting valve seat, and there is a gap having a width exceeding 10 μm between the stem of the valve body and the wall in the valve guide of the opening / closing valve. .

  The cross-sectional dimension of the nozzle mouth is typically the diameter of the circular nozzle mouth.

  According to a further embodiment of the invention, the charging system is characterized in that the control unit includes a local control box for each cylinder and controls the timing and charging of all injectors per cylinder.

  According to a further embodiment of the invention, the dosing system is characterized in that 4 to 10 injectors are used for each cylinder.

  According to a further embodiment of the invention, the dosing system is characterized in that it comprises a local accumulator for each injector or for every injector connected to an individual cylinder.

  According to a further embodiment of the present invention, the dosing system includes an outlet for each injector to connect with the return line to direct excess oil to the lubricating oil source or to perform pressure measurements. It is characteristic that it has.

  According to a further embodiment of the present invention, the dosing system includes each injector made as a unit, the open / close valve includes a ball valve body and an interacting valve seat, the valve body stem and the valve guide for the open / close valve. It is characterized by a gap having a width exceeding 10 μm between the inner wall and the inner wall.

  According to a further embodiment of the present invention, the injection system is such that each injector is made as a unit, and the on-off valve is an electromechanical valve built into the injector for injection of lubricating oil, The mechanical on-off valve is characterized by including a spring-loaded valve stem.

  According to a further embodiment of the invention, the dosing system includes a flow measuring unit having the same operating range for each injector and each cylinder, the control unit being connected to all the flow measuring units and relatively It is characterized by being suitable for receiving a signal from the flow rate measuring unit with an injector at a large flow rate and receiving a signal from the central flow rate measuring unit of the cylinder at a relatively small flow rate.

  According to a further embodiment of the present invention, the dosing system includes a flow measuring unit having a different operating range for each injector and each cylinder, and the control unit is connected to all the flow measuring units for minimal operation. The flow rate measuring unit having a range is a local flow rate measuring unit connected to the injector, and the flow rate measuring unit having the maximum operating range is a central flow rate measuring unit of the cylinder.

  According to a further embodiment of the invention, the dosing system is characterized in that it simply comprises a single cylinder central flow measurement unit coupled with at least one local flow measurement unit connected to the injector.

  According to a further embodiment of the invention, the dosing system is characterized in that it comprises a combination of a local flow measuring part of the cylinder and a local flow switch of the injector.

  According to a further embodiment of the invention, the method is characterized in that a local flow measurement of the injector is performed in combination with a central flow measurement for each cylinder. In this way, measurement results from individual injector local flow meters can be used with relatively large flow rates, with low flow rates (eg, at low engine speeds and small input volumes). Rather than using a flow meter in the center of the cylinder, more accurate measurement is achieved. The reason for this is that the input per injector needs to “cover” a relatively wide area.

  Another example would be that instead of using the same flow meter (with the same capability), different flow measuring units with different flow ranges may be used. Here, the flow rate measuring unit having the minimum flow range is located locally on each injector, and the flow meter having the maximum flow range is located in the center of the cylinder. This method provides that the flow measurement system can easily provide accurate flow measurements throughout the entire flow range.

  Another example would be to combine a minimum one flow meter mounted on one of the injectors with a central flow meter. By doing so, we can provide a measurement system that can handle not only small flow rates but also large flow rates, providing a cheaper and less maintenance-friendly configuration when the number of flow meters is limited can do.

  According to a further embodiment of the invention, the method is characterized in that the supply pressure in the supply line is monitored.

  According to a further embodiment of the invention, the method is characterized in that the supply pressure in the supply line is used as a parameter for controlling the input.

  According to a further embodiment of the present invention, the method comprises the use of an electromechanical valve integrated in the injector for moving the valve stem of the on-off valve by injecting the lubricating oil in order to inject the lubricating oil. It is characterized in that the lubricating oil is charged by operating a type on-off valve.

  According to a further embodiment of the invention, the method is characterized in that the timing and the input amount are controlled by the opening and closing time of the electromechanical valve.

  According to a further embodiment of the invention, the method comprises a flow measuring unit having the same operating range set for each injector and each cylinder, and the control unit is connected to all flow measuring units, Is characterized in that the measurement from the injector is selected and the measurement from the central flow rate measurement part of the cylinder is selected with a relatively small flow rate.

  According to a further embodiment of the present invention, the method comprises a flow measuring unit having a different operating range for each injector and each cylinder, and the flow measuring unit having the smallest operating range is connected to the injector. The flow rate measuring unit selected as the local flow rate measuring unit and having the maximum operating range is selected as the central flow rate measuring unit of the cylinder.

  According to a further embodiment of the invention, the method is characterized in that only a central flow measurement of one cylinder is performed, which is combined with at least one local flow measurement at the injector.

  According to a further embodiment of the present invention, the method performs the flow measurement as a combination of a local flow measurement of the cylinder by the local flow measurement unit of the cylinder and a local flow registration of the injector by a local flow switch of the injector. It is a feature that it is done.

  Furthermore, the injector is characterized in that the valve seat is conical.

  Further, the injector is characterized in that the gap region corresponds to at least the entire region of the nozzle opening of the injector.

  Further, the injector is characterized in that the injector includes a filter and the gap of the on-off valve has the same width corresponding to at least half the mesh width of the filter.

  Furthermore, the injector is characterized in that it comprises an electromechanical actuator, preferably in the form of an electromagnetic valve or a piezoelectric element.

  Furthermore, the injector is characterized in that it has a discharge port for connection with a return line in order to discharge excess oil or to perform pressure measurements.

  In addition, the injector is characterized by a flow check window or flow switch for the injector to visually or electrically indicate the actual flow rate.

  Furthermore, the injector is characterized by being suitable to operate at a supply pressure between 3 MPa (30 bar) and 10 MPa (100 bar).

  Furthermore, the injector is characterized by being suitable for operation with one or more compact jets.

  Furthermore, the injector is characterized by being suitable for operation with one or more mist sprayers.

  Furthermore, the injector is characterized in that the gap width between the stem of the valve body and the boring in which the stem is received is at least half the size of the cross-sectional dimension of the nozzle opening.

  For each injector or all injectors connected to the cylinder, the pulsating flow is measured simultaneously.

  If one injector fails, other injectors can automatically complement / replace one or more failed injectors based on control in the controller and closing adjustment.

  In parallel with the design of the control so that the transported quantity can be controlled based on the actual consumption / flow rate, it is preferable to have an opening / closing function for the charging part built in the injector. Yes, this eliminates uncertainty due to viscosity (temperature, oil type), supply line distance, and diameter.

  Built-in opening and closing so that only one common supply line of pressurized lubricant (no need for return line) simplifies to appreciably both cable piping and drawers The basic concept of using a valve, preferably an injector with an electromagnetic valve, defines that the input is proportional to the opening time of the open / close electromagnetic valve. Preferably there is a separate local control box used to open and close the injector based on signals from the ship's engine / control.

  Electromechanically tuned injectors designed for cylinder lubrication of large diesel engines inevitably have advantages over prior art lubrication systems. Systematically, individual adjustments can be made regarding the amount and timing of the lubricant.

  This function relies only on a control box that can control each single injector individually or together in terms of timing and open time. This may occur separately from the other open / close valves and is limited only by the speed at which the open / close valve in the injector can perform the open / close cycle.

  The measured flow rate is used to control the conveyance amount with respect to the planned amount. Due to the predetermined size deviation during the predetermined period, the linked local control box can modify the open time for one or more solenoid valves for the linked injector.

  The injector is not damaged by particles that are smaller than the nozzle opening and larger than the gap width. Thereby it is possible to work with a relatively coarse filtration of the oil. Even if the oil contains small particles with a size of 10 μm or more, there is no risk of clogging the valve body / ball. It has no problem to operate with a gap width of 10 μm to 0.3 mm or more in the opening and closing valve. The seat in the valve is typically conical and is designed as a seat in the check valve, and the hydraulic pressure in the valve keeps the valve closed along with the closure / spring.

  Particles larger than the gap width (valve body / valve stem radius and the valve on which the valve stem is placed so that the valve stem can be tilted or moved to an off-center position where the valve seat and valve stem are not aligned. Even when entering the valve (measured as the difference (radius difference) between the housing bore radius), the ball shape will ensure that the valve continues to tighten.

  The tilt position may be caused by engine vibration in some cases. This tightness is also ensured by the relatively large gap opening between the valve body and the wall in the boring.

  The only important wear surface is the valve seat, which is self-adjusting, providing high reliability of the valve function within the injector.

  Other embodiments may mean that an indirect method for determining flow is used instead of using a flow measurement unit with direct measurement of flow. For example, it would be possible to use a flow measurement unit that uses a flow switch (flow monitor) that is assumed to be constant in pressure and temperature so that the signal duration can be measured. Thus, a signal proportional to the input amount is provided to the control unit. For example, such other embodiments can be provided in the form of a flow meter where the ball is lifted off the ball seat and a sensor is attached for detection of this condition. In order to perform a measurement independent of the viscosity, it may be necessary to incorporate a flow measuring unit in a box having a constant temperature, for example, by thermostat temperature control.

  Other embodiments provide local flow switches (flow monitors) for some injectors to ensure that all measurements of consumption are taken while simultaneously providing that flow is present in all injectors. In combination with this, the input system will be designed so that a central flow measuring unit for each cylinder is used. In this way, only monitoring of the total flow into the cylinder is performed, and a simple flow switch (typically one for each injector) where the local flow measurement section simply indicates the presence or absence of flow. When replaced, flow measurement of the input system is simplified. The flow rate measurement unit is connected to a control unit or local control box that controls the injector for the individual cylinders, where the planned flow rate and the actual flow rate are compared here. In the case of deviation, a flow switch can be used to take into account whether some injectors have ceased operation.

  Another embodiment for the above injection system is that the controller or the local cylinder control box can provide a flow switch signal between the various injectors coupled to the same cylinder, in addition to measuring the actual total consumption per cylinder. At the same time, it may be to trigger a warning or alarm to the user if a deviation exceeding any value occurs, for example, the flow rate signal is 20% for some time.

  Another use of the above flow signal may be to measure the period from the operation of the injector to the start of a flow meter flow pulse. This measurement is compared with a system specific inspection measurement of the time that elapses between the operation of the injector and the start of injector injection. In speculative terms, both measurements will be fairly close to each other so that the signal from the flow measurement unit can always be used directly without any problems. In this way, it is possible to control whether or not the timing when the deviation reaches an arbitrary value (that is, the time for operating the solenoid) must be adjusted.

  Further possible embodiments of the dosing system may include a flow measuring unit in the form of a conventional elliptical rotor-based flow measuring unit. The disadvantages of this type of measuring section are typically not suitable especially for large flow ranges, since a certain amount is required to operate the rotor once, thereby causing signal emission. That's what it means. This is in addition to the fact that the pulsating conveyance of the lubricating oil does not result in a uniform operation of the flow rate measuring part. It may be required to change the time period during which pulses are counted in order to obtain some available measurement. Starting from the expected flow rate, the local control box is for changing the period during which the flow pulses are counted, and at the same time preferably performing continuous calculations with continuously overlapping periods. For a given flow measurement unit, a correlation between a given flow interval and the number of pulses should be set based on empirical experiments and should be integrated into the local control box.

  The cylinder is used between 4 to 10 injectors depending on the size and type of the engine.

  The dosing system is operated by a pressurized supply line with lubricating oil. The lubricating oil is maintained at a constant pressure. And, in connection with minimizing obstructions / variations in the pressurized supply line for individual cylinders / injectors, there may be a need to place accumulators centrally on a per cylinder and / or per injector basis. Good.

  Instead, for the use of accumulators in the system, the supply pipes can be used with large separation distances so that the pipes become accumulators alone. The timing of supplying the lubricating oil is controlled locally or centrally.

  The timing of supplying the lubricating oil is controlled locally or centrally. The start-up time is continuously adapted according to the engine reference signal.

  Various solutions can be used to monitor the function of the injector. First, a parallel flow measurement is used in which the actual input is compared to the expected flow. This flow measurement can be carried out centrally for each injector or locally for each cylinder so that the actual input can be used for closing adjustment.

  In the case of deviations, these are processed / handled by the local control box or the central control box, respectively. For example, control can identify any problem with one or more injectors.

  In combination with the above flow measurement, the supply pressure can be monitored in the pressurized supply line.

  Another embodiment may be that the flow measurement unit can be used locally as well as having additional control in the form of a central flow measurement unit.

  It should be noted that to some extent the system may compensate for changes in pressure, so that the transport amount can be individually adjusted as individual opening and closing times.

  Other embodiments provide for injectors for cylinders (with injectors or individual control boxes per cylinder), for example, at individual lubrication points, or in some cases via control boxes in the center of the cylinder. It is possible to guarantee the handling of errors with each other in a form that increases.

  In response to a reference signal from the engine (load, flywheel position, etc.), the control box controls the timing and input of one or more injectors per cylinder.

  Local control boxes can be provided directly connected to the injectors, or alternatively can be integrated into individual injectors.

  The input is calculated from feed rate, selection of adjustment algorithm, oil analysis and other engine specific parameters, sulfur percentage, fuel type (residual TBN, Fe content, etc.). These parameters are read automatically and directly or indirectly via a central controller.

  Alternatively, the minimum amount of lubricant to be supplied to the cylinder may be determined based on the entire area of the cylinder lining or exclusively based on the area under the injection valve. The latter half of the transport and starting point is then found in particular as a function of the area situation in the cylinder, optionally combined with some of several other parameters.

  Alternatively, waste oil analysis can be used as an active control parameter. Waste oil analysis can be performed online or manually, and in this context, the amount of lubricating oil is adjusted in proportion to the content of Fe particles. Then, if this cannot improve the measured value within a predetermined time, an alarm is issued.

  Alternatively, an analysis of the remaining TBN online measurements may be used directly for transport adjustment or as a combination of increased lubricant volume and transport changes.

  The injector according to the invention is equipped with a ball valve body and an interacting valve seat which is typically conical but can also be formed in a shape corresponding to the ball shape. Sealing ensures that the gap area is not a flow restriction even with a large gap area, so that the total nozzle area is used in the case of several nozzle openings per injector. It means to correspond at least to the area.

  In practice, this means that the gap is only as large as 0.005 mm, since particles of about 0.01 mm can press the valve body against one side and the gap width can be increased to 0.01 mm. It can mean that it can be done. Thereby, since the ball body fits to the seat, a path of particles having a size of 0.01 mm is possible without obstructing the operation of the valve body and without leaking the valve.

  However, since the injector nozzle mouth is typically 0.3 mm or greater, the gap width (radius difference) will typically be approximately 0.15 mm or greater. Similarly, the filter can be coarser depending on the size of the nozzle opening and can tolerate large particles.

  With the ball valve type, it can operate in a reliable manner even with a large gap with a certain distance between the stem and boring of the valve body so that the boring does not appear as a valve guide for the valve stem Therefore, it is possible to prevent dirt and particles from blocking the operation of the valve body. Such a wide gap would not be suitable for applying a needle valve.

  Creating an injector is easy without precision tolerances and complex mounting.

  The installation of the dosing system is also simple since all that is required is a common supply line for each cylinder. All injectors are connected to this supply line. There is no need for a return line because each injector is simply electrically connected to a common control box that can be locally attached to individual cylinders. This provides maintainability and high reliability.

  The solenoid in the solenoid valve can be a standard solenoid as used today. The injector has low power consumption because only the amount of lubricant required is pumped up to the pressure level for injection.

  By extending the system, a special embodiment that may include sensors that can measure pressure, temperature, or take oil samples for analysis, it is possible to make the injector more intelligent. The pressure provides information about piston position determination and knowledge about the load on the engine. Temperature represents several things related to the conditions in the cylinder. Oil samples can form the basis for evaluation of lubrication conditions. In the background of the data, the injection time and period can be calculated from a predetermined control algorithm in the control unit.

  This, on the one hand, allows the injector to continue its operation on data that has already been defined due to a network failure, while at the same time limiting the possibility of one or more injectors failing simultaneously, thus achieving the highest possible multiplicity. The

  Since the injector is self-adjusting, it is easy to install and replace the injector.

  Each injector has its own time control input, where the timing and input amount are controlled by the injector opening and closing time.

  The injector may comprise a spray valve or a valve with one or more spouts / compact spouts. Injectors can be made in embodiments that only supply pressurized lubricant without a return line. Typical supply pressures are 3 MPa (30 bar) to 10 MPa (100 bar).

  The valve function of the injector is a ball valve.

  For example, the injector can be electromechanically started in the form of an electromagnetic valve or a piezoelectric mechanical component.

  Another embodiment may be that the injector is equipped with a flow check window or flow switch for visually or electrically indicating the actual flow. In this way, a direct display of individual injectors that are operating and functioning is provided. In some engines, individual injectors are placed in difficult-to-access locations, where they may be useful for electronic monitoring that is detected locally but reported centrally. An example of such a solution may be a conical boring in a ball control glass in which a sensor for detecting the ball is arranged.

And it can be said that the advantage of this invention includes the following, among others.
Viscosity independent injector / lubrication system.
Simplified injector design.
Simplified system for installation and maintenance.
A robust and flexible system that is not affected by a single failed injector.
The feasibility of optimizing the amount of spray / lubricating oil in the individual injectors, and thereby the integrated optimization of the individual injectors (in each case too little and (Not too many) feasibility.

  The present invention will now be described more precisely with reference to the accompanying drawings.

1 shows a schematic view of a dosing system according to the present invention. 2 shows a further embodiment of the system according to the invention. 2B shows details of the system shown in FIG. 2A. 2 shows a further embodiment of the system according to the invention. Fig. 2 shows a detailed view of an injector used in the system according to the invention. 4 shows another embodiment of an injector used in a system according to the invention.

  FIG. 1 shows a comprehensive lubrication system for N cylinders 1. Each cylinder is equipped with a plurality of X injectors 2 connected to a common lubricating oil supply line 31 having a constant supply pressure of, for example, a size of 3 MPa (30 bar) to 10 MPa (100 bar). The supply pressure supplied from the day tank 1000 is conveyed by the hydraulic pump unit 10.

  The pump station 10 includes two pumps 11, two filters 12 and two check valves 13 that prevent lubricant from returning through the stationary pump 11. The pump station also includes two shut-off valves 14 that are inserted into the supply line 34 so that the filter 12 is flushed during operation. The two pumps 11 are spares for each other and are automatically started when the hydraulic pressure decreases.

  The end of the supply line 31 is provided with a pressure valve 20 or a pressure valve 115 (in the figure, the latter is shown in principle) which can be electronically controlled in a stepless manner. Typically, the pressure in the supply line is constant, where a common pressure valve 20 is used when the pressure is constant. Instead, various supply pressures may be used depending on the amount to be charged, such as the time available for transportation (eg, 3-6 crank degrees to hit the piston), the viscosity status (oil type and temperature), etc. As can be used, the supply pressure in the supply line 31 can be used as an additional parameter for the system.

  As shown in FIG. 1, the pressure valve 20 can be an electronically controlled pressure valve with adjustable pressure via a connection 505 to the general control 200 or possibly to the cylinder local control box 100. This adjustable pressure can be used for the amount of lubricating oil input as a parameter.

  Each cylinder comprises a branch pipe 22 connected to a main supply 31. On the branch pipe 22, a flow rate measuring unit 4 for measuring the amount of lubricating oil actually supplied is attached. The signal from the flow rate measuring unit 4 is transmitted to a local control box 100 where the measured value is compared with the expected flow rate, and depending on the magnitude of the deviation, the control box 100 opens the individual injectors 2 for the corresponding cylinder. You can adjust the time.

  An electromechanical valve with a solenoid 1014 is mounted on each injector 2. By operating the solenoid 1014, the injector is opened and the lubricating oil is conveyed. The conveyance amount of the lubricating oil is proportional to the period during which the valve continues to open. However, this assumes that the pressure in the supply line is constant, and for this purpose an accumulator 6 is provided.

  A local control box 100 for controlling the open / close time for all the injectors 2 to be connected is provided for each cylinder. By operating the injectors 2, the lubricating oil is guided from the branch pipes 22 of the supply lines 31 through the flow rate measuring units 4 and the branch lines 21 of the respective injectors 2. The flow measuring unit 4 that directly or indirectly measures the passing flow is connected to a local control box 100 where a comparison between the expected flow and the actual flow is performed, and possible corrections are calculated, the injector's The open time for the solenoid 1014 is adjusted. In the embodiment shown, the accumulator 6 is provided with a flow measuring unit 4 and a branch piece 21 to ensure a uniform flow rate over the flow measuring unit 4 that otherwise impedes flow measurement in the lubricating oil. Will be provided in order.

  All the control boxes 100 specific to the cylinders are connected to the main control box 200. From the main control box 200, operation information (for example, a planned amount of lubricating oil) is transmitted to all the connection portions via the signal cable 550 or the network. In the same way, each local control box 100 also obtains information about flywheel position via signal cable 601 and based on operational data from the main control box 200, the exact opening time and the associated opening period. Is controlled. In case of an error, the local control box 100 activates an alarm sent via the signal cable 650 and via the network.

  The main control box 200 receives and transmits information from the marine engine regarding actual load, feed rate, hydraulic pressure and temperature, and rotation, and based on this information, an accurate startup time is calculated.

  Instead of the embodiment shown in FIG. 1, it would be possible to replace the local cylinder control box 100 with a main control box 200 in the center of the engine. This will require all cylinder or injector specific flow measurement signals to be sent to the main control box 200 and thus the main control box 200 to control all of the injectors. This procedure will simplify the control system. However, it will require a fairly extensive cable drawer. In particular, this variant may be available on a small and compact engine.

  In addition, this embodiment provides that the flywheel reference signal (via signal line 601) and the load / index signal (via signal line 501) all generate possible warning signals (via signal line 506). It will need to be transported directly to the main control box 200. In a variation of this embodiment, the individual injector solenoid valves 1013 would be actuated directly from the main control box 200 via the signal line 120 to control the opening and closing of the solenoid valves in common, individually or both. . The warning signal is generated directly by the main control box and sent via the signal line 650 to the ship's warning system.

  2A and 2B show that the cylinder local control box 100 is integrated into the individual injector 2 instead, with the intention that the local control box 100 of the cylinder is replaced by the local control box 101 of the injector. The modification of embodiment of a case is shown. This is because the local individual flow measurement unit of the injector 4. X, that is, one flow rate measuring unit for each injector 2, and a flow rate measuring unit 4. It is necessary to use possible individual accumulators placed between X and the injector (this embodiment is not shown in FIGS. 2A and 2B, where only one local accumulator 6 is shown per cylinder) It is good.

  The embodiment shown here is identical to the system described in FIG. That is, the main control box 200 is also used here. The main control box 200 here only processes the signals from the individual injectors and is no longer a signal for the cylinders.

  FIG. 3 shows that the injector 1014 is actuated at a time via a cable 120 that continuously connects all the solenoids 1014 on the injector associated with the same cylinder (coupled to the cylinder concerned). Fig. 5 shows another embodiment when all are activated simultaneously. In this embodiment, there is a cylinder local control box 100 that controls all injectors to which the cylinder local flow measurement and possible accumulators are applied. This means that the system is further integrated and simplified.

  Another possible embodiment is that instead of the local control box 100 of the cylinder described in FIG. 3, the local control box of one injector is based on the local flow measurement of one cylinder and the remaining injectors. Can be controlled. As described with respect to FIGS. 2A and 2B, this variation would mean that the local control box of one cylinder is replaced with the local control box of one injector. One such embodiment would be absolutely simplest with minimal cables, flow meters, etc.

  Basically, it is also possible, for example, that a local control box of two or more injectors controls all the injectors for one cylinder independently of all others. Combining this with the monitoring function in the local control box 101 of the active injector, for example, a proxy function that a subsequent injector is commanded to take over via a relay connection and cable, for example, due to an error in the preceding injector A system can be constructed. An injector local control box can then be created to trigger an alarm if the injector local control box fails simultaneously when the preceding injector fails.

  FIG. 4 shows an injector that can be used in a system of the kind described above. On the figure, it is shown that each cylinder 1 has several injectors 2 (four shown for each cylinder in the figure). The pressurized oil is supplied to the injector 2 through the supply pipe 20100 through the branch pipe 21.

  The injector shown in FIGS. 4 and 5 includes a nozzle 1001 attached to an internal valve housing 1006 via a male screw thread. The valve housing 1006 itself has a flange that rests partially on the injector container 1017 itself and partially rests on the assembly flange 1007. The injector container 1017 is provided outside the assembly of the nozzle 1001 and the valve housing 1006, where the injector container 1017 is mounted in the flange, for example by an interference fit. At the top, the inner valve housing 1006 consists of a flange with an O-ring shaped groove, and subsequent rotation keeps the valve housing 1006 traveling a distance into the solenoid core / armature vessel 1009. The O-ring 1008 ensures that pressurized oil remains in the valve housing 1006 and the solenoid core / armature vessel 1009. Around the solenoid core / armature container 1009, a main flange 1010 for clamping an injector container having a nozzle via a screw 1011, a solenoid core / armature container 1009, and an assembly flange 1007 are provided. Nozzle / valve housing assemblies 1001/1006 are installed in the injector container and the O-ring 1002 ensures that dirt or oil residue does not further enter the injector container 1017.

  In the solenoid core / armature container 1009, an armature / piston 1012 having a female thread is installed, where a valve body 1003 is attached, and a threaded joint is fixed by a tapered screw 1013. Within the armature 1012, there are several paths 1023 for directing pressurized oil in the direction toward the nozzle. Possible movement of the valve body / armature 1003/1012 is provided from the cavity 20200.

  In the injector 2, oil is guided through the injector through the cavity 20200 and through the path 1023. Thereafter, the oil continues to enter the cavity 1020 through the path 1021 from outside the cavity 1022 and from where the oil is directed to the cavity around the ball valve seat 1019 via the gap 1030. A gap is formed between the valve body stem 1003 and the wall 1031 in the bore where the valve body stem is received.

  When the solenoid 1014 is activated, the valve body 1003 is moved in the opposite direction of the solenoid 1014 until the cavity 20200 is filled with the armature / piston 1012. When the valve body 1003 having the built-in ball 1016 is lifted from the ball seat 1019, the pressurized oil is guided to the outside through the nozzle seat 1019 through the valve seat 1019 through the path 1018. When the electrical signal direct line 120 from the control box 100 to the injector solenoid 1013 is switched off, the spring 1005 presses the valve body 1003 and the armature / piston 1012 in the opposite direction of the ball seat 1019. , Ensures that the injector 2 / ball seat 1019 is closed.

  The spring 1005 shown in FIG. 4 ensures that the valve closes when the solenoid 1013 is switched off. FIG. 4 shows that the spring force can be adjusted by adjusting the compression of the spring by setting the position of the nut 1004. In practice, the required spring force to provide a sufficiently quick closing of the valve can be determined by empirical experiment as a compromise found between the solenoid force and the spring force. Thus, compression is constant and the “nut” is integrated into the valve body in the form of a rest / collar supported by a spring.

  When the ball seat 1019 closes again, the pressurized oil in the supply path 20100/20200 will act on the valve body 1003 so that both the spring 1005 and the hydraulic pressure continue to close the injector ball seat 1019.

  The valve function of the injector is executed by a ball valve body as shown in FIG. It is possible to use an injector that sprays and / or forms an oil spout and to use an injector with one or more nozzle ports 1040.

  The injector is controlled by an electrical signal 120 that allows free and independent control when the injector / valve opens and closes, thereby controlling the open period.

  FIG. 5 functionally corresponds to the system of FIG. 4, but basically shows a system comprising another embodiment of an injector. Here, it is possible to provide pressure measurements or samples of possible lubricant residue from the cylinder through the outlet 20000 on the side of the flange. Outside the nozzle / valve housing 1001/1006, the injector has a gap with respect to the injector container 1017 and communicates with the outlet 20000 through this gap.

Claims (19)

An injection system for cylinder lubricant into a large diesel engine cylinder, for example a marine engine,
A lubricant supply that may be constituted by a pump station or an accumulator;
A supply line from a lubricant supply source;
Corresponds to the number of cylinders of the engine or engines having an inlet, an on-off valve part, and one or more nozzle ports for injecting cylinder lubricant into the connected cylinders and connected to the supply line With some injectors,
In a charging system including a control unit that controls each on-off valve unit,
The charging system includes a flow rate measuring unit for each injector and / or for each cylinder, the flow rate measuring unit is connected to a control unit used in closing adjustment, and a plurality of signal cables are connected to the engine. Is connected to the control unit so as to convey the load / index signal directly to the control unit so as to control the timing and input amount of one or more injectors for each cylinder according to the reference signal of Each injector is made as one unit, and the opening / closing valve section is an electromechanical valve built in the injector for supplying lubricating oil, and the electromechanical opening / closing valve is a spring-biased valve stem. An input system characterized by including:   The injection system according to claim 1, wherein the control unit includes a local control box for each cylinder, and controls timing and injection of all injectors for each cylinder.   4. The charging system according to claim 1, wherein 4 to 10 injectors are used for each cylinder.   The charging system according to any one of claims 1 to 3, wherein a local pressure accumulator is provided for each injector or for every injector connected to an individual cylinder.   5. An injector according to claim 1, wherein each injector has an outlet for connection with a return line, in order to introduce excess oil to the lubricating oil supply or to perform pressure measurements. The input system according to claim 1.   Each injector is made as one unit, and the opening / closing valve portion includes a ball valve body and an interacting valve seat, and is 10 μm between the stem of the valve body and the wall in the valve guide of the opening / closing valve portion. 6. The dosing system according to any one of claims 1 to 5, wherein there is a gap having a width exceeding.   The charging system includes a flow rate measuring unit having the same operating range for each injector and each cylinder, and the control unit is connected to all the flow rate measuring units, and the injector has a relatively large flow rate at the injector. It is suitable for receiving a signal from the flow rate measuring unit and receiving a signal from the central flow rate measuring unit of the cylinder at a relatively small flow rate. Input system.   The charging system includes a flow rate measuring unit having different operating ranges for each injector and each cylinder, the control unit is connected to all the flow rate measuring units, and the flow rate measuring unit having the minimum operating range is an injector. The input according to any one of claims 1 to 6, wherein the flow rate measurement unit connected to the flow rate unit having the maximum operating range is a central flow rate measurement unit of the cylinder. system.   9. The charging system according to any one of the preceding claims, characterized in that the dosing system simply comprises a single cylinder central flow measurement unit coupled with at least one local flow measurement unit connected with an injector. The input system described in 1.   7. The charging system according to any one of claims 1 to 6, wherein the charging system includes a combination of a local flow rate measuring unit of a cylinder and a local flow rate switch of an injector. In a method for injecting cylinder lubricant into a large diesel engine cylinder, such as a marine engine,
Pressurizing lubricating oil in a lubricating oil source, which may be constituted by a pump station or accumulator;
Directing the lubricating oil from the lubricating oil source through the supply line;
Injecting lubricating oil through several injectors having an injector connected to the supply line and having an inlet into a coupled cylinder, an on-off valve portion, and one or more nozzle ports;
Controlling each on-off valve unit by a control unit,
Transmitting the result of the flow measurement to the control unit by means of local flow measurement for each injector and / or central cylinder flow measurement of the actual oil input per injector;
Comparing the flow measurement of the expected or planned oil quantity with the actual oil input, and
Conveying a load / index signal directly to the controller to control the timing and input of one or more injectors per cylinder in response to a reference signal from the diesel engine;
The control unit transmits a control signal to the opening and closing unit for adjusting the timing and amount of oil to the required range,
In order to move the valve stem of the on-off valve part by injecting the lubricating oil, the on-off valve part is operated in the form of an electromechanical valve built in the injector so that the lubricating oil is injected. A method characterized in that an input of is performed.   12. The method according to claim 11, wherein a local flow measurement of the injector is performed in combination with a central flow measurement unit for each cylinder.   13. A method according to claim 11 or 12, characterized in that the supply pressure in the supply line is monitored.   14. The method according to claim 13, wherein the supply pressure in the supply line is used as a parameter for controlling the input amount.   The method according to any one of claims 11 to 14, wherein the timing and the input amount are controlled by the opening and closing time of the electromechanical valve.   A flow rate measurement unit having the same operating range is set for each injector and each cylinder, and the control unit is connected to all the flow rate measurement units, and a measurement from the injector is selected by a large flow rate and compared. 16. A method according to any one of claims 11 to 15, characterized in that the measurement from the central flow measuring part of the cylinder is selected with a small flow rate.   A flow rate measuring unit having a different operating range is set for each injector and each cylinder, and a flow rate measuring unit having a minimum operating range is selected as a local flow rate measuring unit connected to the injector, and has a maximum operation. 16. A method according to any one of claims 11 to 15, characterized in that a flow measuring part with a range is selected as the central flow measuring part of the cylinder.   18. Only one central flow measurement of one cylinder is performed, and the central flow measurement of one cylinder is combined with at least one local flow measurement at the injector. The method described.   18. The flow rate measurement is performed as a combination of a local flow rate measurement of the cylinder by the local flow rate measurement unit of the cylinder and a local flow rate registration of the injector by a local flow rate switch of the injector. The method according to any one of the above.

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