KR102002181B1 - System and method for dosing cylinder lubrication oil into large diesel engine cylinders - Google Patents

Abstract

The present invention relates to a system and a method for dosing a cylinder lubricating oil to a large diesel engine cylinder, for example a marine engine, comprising: - a lubricating oil supply part composed of a pump facility or an accumulator; A supply line from said lubricating oil supply; A plurality of injectors having an inlet, an opening and closing valve device and at least one nozzle hole for injecting the cylinder lubricant into the associated cylinder, said injector being connected to said supply line and corresponding to a plurality of cylinders in said engine or multiple engines; And a control device for controlling each on-off valve device. In order to overcome the disadvantages of dependence on flow rate and viscosity in the feed line, the system is characterized in that the dosing system comprises a flow measuring device for each injector / respective cylinder and the flow measuring device is a control device And the like.

Description

TECHNICAL FIELD [0001] The present invention relates to a system and a method for dosing a cylinder lubricating oil for a large-sized diesel engine cylinder,

The present invention relates to a system for dosing a cylinder lubricant to a large diesel engine cylinder, for example a marine engine,

- a lubricating oil supply consisting of a pump or accumulator;

A supply line from said lubricating oil supply;

A plurality of injectors having an inlet, an opening and closing valve device and at least one nozzle hole for injecting the cylinder lubricant into the associated cylinder, said injector being connected to said supply line and corresponding to a plurality of cylinders in said engine or multiple engines; And

- a control device for controlling each on-off valve device.

The present invention also relates to a method of administering a cylinder lubricating oil to a large diesel engine cylinder, for example a marine engine,

- pressurizing the lubricating oil to a lubricating oil supply which may consist of a pump facility or an accumulator;

- transferring lubricant from the lubricant supply through the supply line;

- injecting lubricant into the associated cylinder through a plurality of injectors having an inlet, an on-off valve and one or more nozzle holes by connecting said supply line with an injector; And

- controlling each on / off valve device with a control device.

In addition, the present invention describes a large diesel engine cylinder, for example an injector for use in a delivery system for a cylinder lubricating oil in a marine engine,

- a lubricating oil supply which can consist of a pump facility or accumulator;

A supply line from said lubricating oil supply; And

An injector each having an inlet for connection to said supply line, said injector having at least one nozzle hole for injecting an opening / closing valve device and cylinder lubricant into an associated cylinder; And

And a control device for controlling the respective on-off valve devices.

The present invention is primarily made for use in electronically controlled injectors wherein the dose is controlled through the valve opening time. This is different from other lubrication systems which generally dose control dose. The dosage of the oil may be sprayed, for example, by direct spray control by having a built-in pump. In system operation, it can be performed mainly with valves that can be controlled by electromagnetic.

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

Prior art solutions based on time-controlled dosing have the disadvantage that their amount is highly dependent on the flow rate and viscosity conditions in the oil feed line.

According to EP 0 049 603 A1, an electromechanical injector is introduced. Flow detectors are used that have integrated switch functions and emit signals when flow is present. The flow rate is monitored by the flow detector and the duration of the flow rate is compared to the manually determined limit value. They are not only able to measure the flow rate, they also control the start and stop of the flow signal.

EP 1 426 571 discloses injector and cylinder lubrication systems. The technique is based on a system in which a solenoid valve is provided for each cylinder and a valve is provided for each valve to open and close for flow. This design has the disadvantage that it is highly required to make the flow and viscosity conditions in the supply line uniform so as to avoid the amount of oil delivered to each of the valves being different. For example, the distance and temperature conditions in the oil supply line must be maintained to be fairly uniform in order to ensure even distribution among all the lubrication points. In practice this is a big problem. The prior art has another disadvantage. To monitor the operation, a pressure sensor is used to monitor the supply pressure to all the injectors. From practical experience, the control knows to recognize the pattern of one or more failed valves. This method strongly requires empirical data used to supervise the injector, and for the same reason uncertainty of this problem is occurring.

EP 1 426 571 discloses a known local injector which basically uses a needle valve as a valve body in the form of a needle and corresponding valve seat. If the needle is inclined with respect to the seat or not aligned with the seat, leakage will occur. So that the guide is guided so that the needles are not displaced radially with respect to the valve seat. This is generally achieved by the fitting of a valve boring (needle guide) with the needle and needle with good immunity. Because they extend through relatively thick cylinder walls and lining, they generally have the disadvantage that the injector must be designed to have a considerable length. The valve seat is closed as close as possible to the nozzle bore to reduce the dead volume so that the valve is actuated / accelerated before starting to deliver oil. This means that the needle is relatively resistant to boring of the nozzle in which the needle is located and that the needle is provided in considerable length to precisely center the needle on the sheet. This means that the valve is sensitive to dust in the piping and lubricant, such as being stuck in a very narrow gap between the needle and the needle guide, with good resistance and fit between the needle guide and the needle, Which means that there is a relatively high demand for purity. This may cause the needles to displace off-center with respect to the seat or cause the movement of the needle to be blocked. In both cases there is a reduction in the function of the valve. This means that there are many requirements for the purity of the oil supplied to the injector.

According to EP 1 582 706, a system corresponding to the systems and methods mentioned by way of introduction is known. This document does not disclose a system including a flow measurement device. Therefore, this document does not disclose how such a flow measuring device can be arranged with respect to the injector and / or the cylinder. Also, this document does not disclose how a flow measuring device can be connected to a control device. Also, this document does not disclose how it can be adjusted based on the signal received by the control device.

JP 2271019 discloses a lubrication system for injecting lubricant into the air / fuel mixture during air intake to mix lubricant and air / fuel mixture before being sucked into the motor. This document relates to a completely different motor technology for small combustion engines. No lubricant is injected into the cylinder through the injector. This document discloses that the controller controls a large amount of lubricant based on the rotational temperature of the sliding parts and the engine. This document does not disclose that it is possible to control the timing and dosing of one or more nozzles that deliver rod / surface signals directly to the control device to inject lubricant into the air / fuel mixture. The system also does not disclose the need to control the timing for lubricant injection according to a reference signal from the engine.

US 4 913 108 discloses a system corresponding to the system disclosed in JP. This document does not disclose any injector for injecting lubricant into the cylinder. This document is for a small combustion engine and involves a significantly different motor technology. That is, it has been disclosed to deliver lubricant to an intake manifold in a vacuum system. Although a flow rate sensor is used to determine the amount of oil delivered from the pump, it does not disclose a sensor that can determine the amount of oil entering a particular cylinder.

In fact, in some cases it may be difficult to ensure sufficient purity of the lubricating oil to be supplied, for example when installing or replacing an injector, or in a stationary state for a long time. In these cases, it is desirable to perform filtration at the feed to the injector corresponding to a typical gap width of 5 to 10 mu m or less, but such fine filtration is difficult to actually set. In general, there may be a problem in setting a stable supply of lubricant so that the filter is not clogged at frequent intervals. In general, the center filter is used for the entire system because the local filter in each cylinder or injector is difficult to install and maintain. In general, there is no problem in the center filtration of the oil, and the clogging of the nozzle holes in individual injectors can be sufficiently avoided. In some cases, a filter / filter is installed locally in the individual injector. However, they are difficult to access and difficult to clean and service. A dosing system for cylinder lubricant is used to install a plurality of electromechanical injectors on the cylinder wall surface and to deliver lubricant to the cylinders. For injectors, these work in conjunction with the needle valve and the following is also true.

- The injector is located through the cylinder lining and possible cooling jets, which means that the distance from the outer contour to the inner cylinder diameter is between 80 and 200 mm. As a result, a long needle is required, and the length of the needle to be guided is proportional to the length of the needle. It is necessary to guide it near the valve seat in relation to the sealing between the needle and the seat. Therefore, a relatively long needle guide appears, and there is a great danger that dust and debris wedges and damages the function of the valve.

- The valve seat in the injector is as close as possible to the nozzle hole of the injector to minimize the dead volume between the nozzle opening and the valve seat.

- There is a need for special design and fabrication requirements and a relatively good resistance to fitting between the needle guide and the valve body / needle in order to ensure that the valve body / needle is precisely centered relative to the valve seat.

In practice, when working with a needle valve, it may be difficult to filter out particles in the lubricating oil to a size smaller than the typical gap used for the needles, for example, 5 to 10 mu m or less. In general, cylinder local filters can be difficult to install and maintain, so use a centered filter for the entire system. In general, there is no problem in filtering out the oil by filtering it locally or centrally with a filter to remove particles larger than 0.01 mm. In actual experience, it is generally shown that only center filters with a mesh width of 0.025 mm or greater can be applied. Such filtration is sufficient to avoid clogging of nozzle holes or holes in individual injectors. A large gap is inadequate to use a needle valve in order to prevent as much as possible the gaps between the needles and the needle guide being blocked from contaminated oil, thus requiring a large gap and a new type of valve body.

It is an object of the present invention to provide a lubricating system and a method of dispensing lubricating oil which can solve the disadvantages of the conventional system.

It is also an object of the present invention to provide an injector capable of solving the disadvantages of the conventional system and being robust / reliable and easy to operate.

In order to overcome the disadvantages of dependence on flow rate and viscosity in the feed line, the system according to the invention comprises a dosing system for each injector and / or each cylinder, the dosing system comprising a closed- In order to control the timing and dosing of one or more injectors per cylinder, in accordance with a reference signal from the engine, in order to transfer the load / indicator signals directly to the control device, And each of the injectors is made as one device, and the opening / closing valve is an electromechanical valve incorporated in the injector for injecting the lubricating oil, wherein the electromagnetic opening / closing valve includes a spring bias valve stem.

The method according to the invention is based on a local flow measurement for each injector and / or a cylinder center flow measurement of the actual dosage of oil per injector per cylinder, sending the result of the flow measurement to the control device, Directing a load / indicator signal to the control device to control the timing and dosing of one or more injectors per cylinder block according to a reference signal from the engine, And the control signal is transmitted to the opening / closing device in order to adjust the timing and amount of the oil to a desired range. In order to move the valve stem of the opening / closing valve by injection of the lubricating oil, By operating an electromechanical valve-type on-off valve integrated in the injector Point is unique.

In this regard, 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. Thus, due to viscosity conditions, possible changes can be made in timing (delay and acceleration of lubricant transfer). Deviations in viscosity conditions are of interest because they can cause very fast or very slow timing for the injection.

The injector includes a valve seat in which the opening / closing valve interacts with the ball valve body, and a gap between the stem of the valve body and the wall surface of the valve guide of the opening / closing valve is 10 占 퐉 or more.

The cross-sectional dimension of the nozzle hole generally refers to the diameter of the circular nozzle hole.

According to a further embodiment of the invention, the dosing system is unusual in that it comprises a local control box for each cylinder in which the control device controls the timing and dosing of all the injectors per cylinder pair.

According to a further embodiment of the invention, it is unusual for the dosing system to use 4 to 10 injectors for each cylinder.

According to a further embodiment according to the invention, the dosing system is characterized in that a local pressure accumulator is provided for each injector or for all the injectors associated with the individual cylinders

According to a further embodiment according to the invention, the dosing system is characterized in that each injector has an outlet for connecting the return line for returning excess oil to the lubricant supply or for performing the pressure measurement.

According to a further embodiment of the invention, the dosing system is characterized in that each injector is made of one device, the on-off valve comprises a valve set interacting with the ball valve body, and the stem of the valve body and the valve guide And has a gap of 10 占 퐉 or more in width between itself and the wall surface in the substrate.

According to a further embodiment according to the invention, the dosing system is an electromechanical valve in which each injector is made in one device, the on-off valve integrated in the injector for dosing lubricating oil, the electromechanical on- - It is unique that it contains a bias valve stem.

According to a further embodiment of the invention, the dosing system comprises a flow measuring device having the same operating range for each injector and each cylinder, said control device being connected to all of said flow measuring devices, Is adapted to receive a signal from the local flow measuring device in the injector and is adapted to receive a signal from the cylinder center flow measuring device at a relatively low flow rate.

According to a further embodiment of the invention, the dosing system comprises a flow measuring device having a different operating range for each injector and each cylinder, said flow measuring device having a narrow operating range, It is unusual that the flow rate measuring device and the flow rate measuring device having a wide operating range are cylinder central flow rate measuring devices.

According to a further embodiment according to the invention, it is unusual for the dosing system to include a single cylinder center flow measuring device in combination with at least one local flow measuring device connected to the injector.

According to a further embodiment of the invention, the dosing system comprises a combination of a cylinder local flow measuring device and an injector local flow switch.

According to a further embodiment of the invention, the method is unique in that the injector local flow measurement is performed in combination with the central flow measurement. In this method, a more accurate measurement can be made, in which relatively large flow rates can be used from the local flow meter in the individual injectors, and a relatively small flow rate (e.g. low engine speed and low dosage) A central flow meter can be used. This is why it is necessary to "cover " a relatively large area of injector per dose.

Other implementations may use other flow measuring devices having different flow ranges instead of using the same flow meter (same capacity), wherein a flow measuring device with a very small flow rate range is locally placed on the individual injectors A flow meter with a fairly large flow range lies at the center of the cylinder. This method shows that the flow measurement system can more easily provide more accurate flow measurements over the entire flow range.

Another implementation would be to combine the central flow meter with injector local flow measurement with at least one flow meter installed in one injector. The method provides a low-maintenance, yet maintenance-free setup measuring system that can adjust large flow as well as small flow rates and has a limited number of flow meters.

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 unusual in that the feed pressure in the feed line is used as a factor to control the dosage.

According to a further embodiment of the invention, the method comprises activating an on-off valve in the form of an electromechanical valve incorporated in the injector to administer the lubricating oil, moving the valve stem of the on-off valve by injection of the lubricating oil, It is unique in that it performs.

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

According to a further embodiment of the present invention, the method is set up with a flow measuring device having the same operating range for each injector and each cylinder, the control device being connected to all of the flow measuring devices, That the measured value from the local flow rate measuring device at the injector is selected by the measuring device and that the measured value from the cylinder center flow rate measurement is selected by the relatively low flow rate.

According to a further embodiment of the invention, the method is characterized in that a flow measuring device with different operating ranges is set for each injector and for each cylinder, and a flow measuring device with a very low operating range is connected to the local flow It is unusual that the flow measuring device selected as the measuring device and having a very high operating range is selected as the cylinder center flow measuring device.

According to a further embodiment of the invention, the method is unique in that it performs only one cylinder center flow measurement and combines it with at least one local flow measurement in the injector.

According to a further embodiment of the invention, the method is characterized in that the flow measurement is carried out by a combination of a cylinder local flow measurement and a cylinder flow measurement device and is performed by a combination of an injector local flow rate registration and an injector local flow rate switch.

In addition, the injector is unique in that the valve seat is conical.

Further, it is unusual that the area of the gap of the injector corresponds at least to the entire area of the nozzle hole of the injector.

In addition, it is unusual that the injector includes a filter and the gap of the opening / closing valve has a width at least equal to half of the mesh width of the filter.

In addition, the injector includes an electromechanical actuator, and is preferably in the form of a solenoid valve or a piezoelectric member.

In addition, it is unusual that the injector has an outlet for connection with the return line for discharging excess oil and performing pressure measurements.

In addition, it is unusual that the injector includes a flow monitor glass or a flow switch for visually or electronically displaying the actual flow rate.

In addition, it is unusual that the injector is adapted to operate at a supply pressure between 30 and 100 bar.

In addition, it is unusual that the injector is adapted to operate with dense jets.

In addition, it is unusual that the injector is adapted to operate as a fog-like spray.

The injector is further characterized in that the gap between the stem of the valve body and the boring receiving the stem receives at least half of the cross-sectional area size of the nozzle hole.

It is linked to the cylinder for each injector or all injectors, and the oscillating flow rate is to be measured simultaneously.

If the injector is faulty, another injector can be automatically supplemented / replaced with one or more defective injectors based on control and closed circuit control in the control unit.

It is desirable to design the control so as to have an opening and closing function of the dosing device incorporated in the injector while at the same time based on the actual measurement of the consumption / flow rate, and it is possible to control the delivered amount and thereby control the viscosity (temperature, oil type) The uncertainty is eliminated because of the distance and diameter of the line.

The basic concept of using an injector with an integrated on / off valve, preferably a solenoid valve, is that the piping and the drawing of the cable are all considerably simpler by having only one common supply line of pressurized lubricant (no need for a return line) , And the administration is proportional to the opening time of the opening and closing solenoid valve. Preferably, the separate local control box used to open and close the injector is based on a signal from the engine / control device of the vessel.

Electromagnetically controlled injectors designed for cylinder lubrication of large diesel engines have the advantage over conventional lubrication systems. That is, the amount and timing of the lubricant can be individually controlled by the system.

These functions depend only on the control box, which can control each single injector separately or together for timing and opening time. This can occur independently of other shut-off valves, and the shut-off valve in the injector is only limited by the speed at which it can perform the shut-off cycle.

The measured flow rate is used to control the amount delivered compared to the planned amount. Due to the deviation of a given size for a given time period, the associated local control box can correct the opening time of the magnet valve for the associated injectors or injectors.

The injector is insensitive to particles smaller than the nozzle hole and larger than the gap width. Thus, a relatively rough oil filtration operation can be performed. There is no risk of valve body / ball clogging even if the oil contains small particles having a size of 10 탆 or more. There will be no problem in operating with a gap width of 10 [mu] m and 0.3 mm or more in the opening and closing valve. The seat in the valve is designed as a generally conical shape, like a seat in a check valve, and the oil pressure in the valve will coincide with the closure member / spring to maintain the valve closure.

Even if a particle larger than the width of the gap (measured by the difference between the radius of the valve body / valve stem and the radius of the boring of the valve housing where the valve stem is discarded is greater than the radius difference) enters the valve, the valve stem tilts to an off- The valve seat and valve stem will not be aligned in line, and the ball shape will ensure that the valve is held tight. The inclined position may also occur due to engine vibration. This rigidity also ensures an opening which is a large gap between the valve body and the wall surface in the boring. Only the critical wear surface is a valve seat that is automatically regulated and provides the injector with considerable reliability of the valve function.

In another embodiment, an indirect method of determining the flow rate is used instead of using a flow rate measuring device that directly measures the flow rate. For example, it is expected that the use of a flow rate measuring device using a flow rate switch (flow rate indicator) will allow the pressure and temperature to be uniform so that the signal period can be measured. Thereby providing a signal proportional to the amount administered to the control device. For example, in this alternative variant, the ball may be provided in the form of a flow measuring device that lifts the ball seat, and a sensor is provided to meter these conditions. In order to make a measurement irrespective of viscosity, it may be necessary to integrate the flow measuring device into a box with a constant temperature, for example a thermostat.

In another embodiment, a central flow rate measuring device per cylinder can be used to design the dosing system, which combines a plurality of injector local flow switches (flow indicators) to obtain the total measured value, Lt; RTI ID = 0.0 > flow. ≪ / RTI > In this way, the flow measurement of the dosing system is simple by performing a monitoring on the total flow to the cylinder, and the local flow measuring device is replaced by a simple flow switch (usually per injector) which simply indicates the presence or absence of flow . The flow measuring device is connected to a control device or local control box which controls the injector for each cylinder, where the planned flow and actual flow are compared. If there is a deviation, the flow switch can be used, considering that some injectors will be shut down.

Another embodiment of the above-mentioned dosing system may be a control device or a local cylinder control box, which further measures the total cylinder consumption per cylinder and simultaneously compares the flow switch signals between the various injectors associated with the same cylinder A given value, for example a deviation of 20% of the time which is a flow rate signal, will cause a warning or an alarm to the user.

Another use of the above-mentioned flow rate signal can measure the time period from the activity of the injector to the flow pulse start on the flow meter. This measurement is compared to a system-specific check time measurement that passes between the injector activities where the injector begins to dispense. By way of extrapolation, all of the measurements can be placed close to each other, and the signal from the flow measurement device can always be used without any problems. In this method, it is possible to control if the deviation has reached a given value, for example if the time for solenoid to be adjusted has to be adjusted.

A further possible embodiment of the dosing system may include a flow measuring device in the form of a flow measuring device based on a conventional elliptical rotor. A disadvantage of this type of measuring device is that it is generally not suitable, in particular for large flow ranges, due to the given amount of rotation required to make one revolution of the rotor. This causes the emission of the signal. In addition to this, the transmission of vibration of the lubricating oil does not provide smooth operation of the flow measuring device. To obtain some useful measurement, it may be necessary to change the period during which the pulse is calculated. Starting at the predetermined flow rate, the local control box will change the period of time during which the flow pulse is calculated, and at the same time will continue to make calculations, preferably in successive overlapping periods. Based on empirical experiments, the correlation between a given flow rate interval and the number of pulses for a given flow measurement device is set to be integrated into the local control box.

For cylinders, between 4 and 10 injectors are used depending on engine size and type.

The dosing system operates through a pressurized feed line with lubricant. It may be necessary to position the lubricant at a constant pressure and towards the center of the accumulator per cylinder and / or the cylinder bore as to minimizing turbulence / deformation in the pressurized feed line in the individual cylinders / injectors.

Alternatively, for the use of an accumulator in the system, this may use a supply pipe that is fairly organized so that the pipe itself is an accumulator.

The timing of administration of the lubricating oil is controlled locally or intensively. The activity time is continuously adapted to the reference signal of the engine.

In order to monitor the function of the injector, various solutions are used. First, a parallel flow measurement is used. Here, the actually dosed amount is compared to the expected flow rate. This flow measurement can be performed locally for the injector or intensively for the cylinder. So that the actually dosed amount can be used for closed-circuit regulation.

In the case of deviations, they are each handled / handled by a local or central control box. For example, the control can identify a problem with one or more injectors.

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

In another embodiment, the flow measuring device can be used locally, as well as having additional control in the form of a central flow measuring device.

To some extent, the individual opening and closing times can be individually adjusted so that they can be compensated for the pressure change and the resulting transmission volume.

As an alternative embodiment, the injector for the cylinder (with a separate control box for the injector or cylinder) ensures the handling of the error at the individual lubrication point or in a form that increases the dose via the cylinder center control box .

The control box controls the timing and dosing of one or more injectors per cylinder in accordance with a reference signal from the engine (rod, flywheel position, etc.).

The local control box can be provided in the direct connection to the injector and can be integrated into the individual injector.

The dosage is calculated from the flow rate, selection of the tuning algorithm, oil analysis, and other engine specific factors, sulfur ratio, fuel type (residual TBN, Fe-content, etc.). These factors are read automatically, directly or indirectly through the central control unit.

Optionally, the minimum amount of lubricating oil to be fed to the cylinder may be determined based on the area under the injector valve, either basically or exclusively by the total area of the cylinder lining. The latter distribution and starting point are found as a function of some of the other parameters and possibly the area conditions in the cylinder combined.

Alternatively, analysis of the endosperm can be used as an activity control parameter. Analysis of the endosperm can be performed either online or manually, and under this background, the amount of lubricant is adjusted in proportion to the content of Fe particles. And if this does not improve the measured value within a given time, an alarm will occur.

Optionally, an analysis of the on-line measurement of the remaining TBN can be used by directly adjusting the dispense or by combining the increasing amount of lubricant with the variation of the dispense.

The injector according to the present invention may be formed in a shape corresponding to the shape of the ball, although the valve seat body and the valve seat installed together with the generally conical, mutually-acting valve seat are generally conical. The sealing is ensured evenly by the large gap area so that the area of the gap does not limit the flow rate. This means that the area of the gap corresponds to at least the entire area of the nozzle hole, so that when there are a plurality of nozzle holes per injector The sum of the nozzle hole areas is used.

In practice, this means that about 0.01 mm of particles can be pressed on one side of the valve body and the gap can be less than 0.005 mm since the width of the gap is increased to 0.01 mm. Thereby, passage of the particles having a size of 0.01 mm would be allowed without valve leakage by not interrupting the movement of the valve body and tightly fitting the ball body to the seat.

Since the nozzle hole of the injector is generally 0.3 mm or more, the gap width (radial difference) may generally be about 0.15 mm or more. Correspondingly, the filter may be coarse and allow large particles depending on the size of the nozzle orifice.

The use of a ball valve type prevents the dust and particles from interrupting the movement of the valve body, where the large gap is such that the bore does not look like a valve guide for the valve stem, And boring. This wide gap can make needle valves unsuitable for application.

The injector is easy to manufacture with little error and no complex installation.

The dosing system is simple to install since a common supply line per cylinder is required. All injectors are connected to these supply lines. There is no need for a return line and only the individual injectors need be electronically connected to a common control box that can be locally installed in each cylinder. This provides serviceability and very high reliability.

The solenoid in the solenoid valve can be a standard solenoid used today. The injector has a low power consumption rate because only the required amount of lubricating oil can be pumped to the pressure level for the injector.

It is possible to make a more intelligent injector in expanding the system, i. E. As a special embodiment, include a sensor capable of measuring pressure, temperature or taking an oil sample for analysis. The pressure provides information about the positioning of the piston and provides knowledge of the load on the engine. The temperature tells what the conditions in the cylinder are. Oil samples can form the basis for evaluation of lubrication conditions. With the background of the data, the injection time and duration can be calculated from the control algorithm given by the control device.

This limits the likelihood of at least one injector failing at the same time to achieve the greatest possible multiplicity, while at the same time the injector will continue its operation with data already given by the failure of the network.

Injectors are self-regulating, making installation and replacement easy.

Each injector has its own dosing device that controls the timing and the amount of time the dose is controlled by the opening and closing time of the injector.

The injector may be provided with a sprayer valve or a valve with one or more jet / dense jets. The injector can be made into an embodiment that supplies only pressurized lubricant and no return line. Typically the feed pressure is between 30 and 100 bar.

The valve function of the injector is a ball valve.

The injector may be electromechanically operated, for example in the form of a solenoid valve or piezo-mechanical member.

In an alternative embodiment, the injector is equipped with a flow monitoring glass or flow switch for visually or electronically displaying the actual flow rate. This method provides a direct indication of the activity and of the individual injectors acting. In some engines, individual injectors are located in difficult-to-access locations, and there may be advantages to have electronic monitoring to locally detect but report intensively. An example of such a solution is a conical boring on a ball control glass on which a sensor for detecting the ball is disposed.

In conclusion, the advantages of the present invention include the following among others.

- Viscosity-independent injector / lubrication system

- Simple injector design

- Easy system - Installation method, maintenance method

- Robust and flexible system that is not affected by one failed injector

- Optimizability integrated into individual injectors as opposed to previous systems where the possibility of optimal amount of spray / lubricant in individual injectors, and thus all injectors are evenly distributed.

1 is a schematic diagram of a dosing system according to the present invention.
Figure 2.1 illustrates a further embodiment of a system according to the present invention.
Figure 2.2 is a detailed view of the system illustrated in Figure 2.
Figure 3 illustrates a further embodiment of a system according to the present invention.
Figures 4.1 and 4.2 are detailed views of an injector for use in a system according to the present invention.
Figure 5 illustrates another embodiment of an injector for use in a system in accordance with the present invention.

The present invention will be described in more detail with reference to the accompanying drawings.

Figure 1 illustrates a complete lubrication system for an N-cylinder (1). Each cylinder is equipped with a plurality of X injectors 2 and is connected to a common lubricant supply line 31 having a constant supply pressure, for example of the order of 30 to 100 bar. The supply pressure is transmitted to the hydraulic pump apparatus 10 supplied from the day tank 100.

The pump facility 10 includes two choke valves 13 which prevent lubricant from flowing back through two pumps 11, two filters 12 and a stationary pump 11. The pump facility also includes two on-off valves 14, which are inserted into the supply line 34 so that the filter 12 can be cleaned during operation. The two pumps 11 lean on each other and automatically start operation when the oil pressure drops.

A pressure valve 20 or an electronically controllable infinite pressure valve 115 is provided at the end of the supply line 31 (the figures generally illustrate the latter). In general, the pressure in the supply line is constant, in which a common pressure valve 20 with constant pressure is used. As another example, the supply pressure can be applied to the supply line 31 as an additional parameter of the system, i. E. The dose, the time it takes to deliver (e. G., 3-6 crank angles to affect the piston) It is possible to apply various supply pressures depending on the temperature and the like.

As illustrated in Figure 1, the pressure valve 20 may be an electronically controllable pressure valve for the general control 200 or possibly the cylinder local control box 100 with an adjustable pressure via connection 505 .

The cylinders are respectively provided to a branch pipe 22 coupled to the main supply section 31. The branch pipe 22 is provided with a flow rate measuring device 4, which measures the actual supply amount of the lubricating oil. The signal from the flow measuring device 4 is transmitted to the local control box 100 which compares the measured value with the expected flow rate and the control box 100 is connected to the individual injector 2 for the cylinder in question, Adjust the opening time for.

Each injector is provided with an electromechanical valve having a solenoid 1014. By operating the solenoid 1014, the injector is opened and lubricant is delivered. The amount of lubricant delivered is proportional to the valve opening time. However, this assumes that the pressure in the feed line is constant and the accumulator 6 is provided for this purpose.

A local control box 100 is provided in each cylinder to control the opening and closing times for all associated injectors 2. The operation of the injector 2 causes the lubricant to flow from the supply line 31 to the branch pipe 22 through the flow rate measuring device 4 and to the respective injectors 2 via the branch line 21 do. The flow measuring device 4, which directly or indirectly measures the flow rate passing therethrough, is connected to the local control box 100, where a comparison is made between the predicted flow rate and the actual flow rate, the possible correction is calculated and the solenoid It is possible to adjust the opening time with respect to the display device 1014. In the illustrated embodiment, the accumulator 6 is provided between the flow measuring device 4 and the branch portion 21 to even out the flow across the flow measuring device 4, Increases and countercurrently interferes with the flow measurement.

All the cylinder specific control boxes 100 described above are connected to the main control box 200. Operating information (e.g., the amount of lubricant) from these main control boxes 200 is transmitted to all the connection devices via the signal cable 550 or the network. In the same manner, each local control box 100 also receives information about the flywheel position via the signal cable 601. Based on the operation data from the main control box 200, the open time is corrected and the associated open period is adjusted. In the event of an error, the local control box 100 generates an alarm and transmits it via the signal cable 650 and the network.

The main control box 200 receives and transmits information from the marine engine about the actual load, feed rate, oil pressure and temperature and changes, and calculates a correction activation time based thereon.

As another example of the embodiment illustrated in FIG. 1, the local cylinder control box 100 may be replaced with an engine centered main control box 200. This would require that a cylinder- or injector-specific flow measurement signal be sent to the main control box 200 in full and the main control box 200 to control all the injectors. This procedure simplifies the control system, but it will rather require pulling the cable extensively. This change can be useful, especially for small and dense engines.

This embodiment also allows all flywheel reference signals (via signal line 601) and load / index signals (via signal line 501) to be generated from where the alarm signal is generated (via signal line 506) It is necessary to be directly transmitted to the main control box 200. As a variation of this embodiment, the solenoid valve 1013 of the injector operates directly from the main control box 200 through the signal line 120 and controls the opening and closing of the solenoid valve: common, individual, or both. The alarm signal is generated directly by the main control box and is transmitted through the signal line 650 to the ship's alarm system.

Figures 2.1 and 2.2 illustrate a variant in which a cylinder local control box 100 is integrated into an individual injector 2 instead of a cylinder local control box 100 to an injector local control box 101 Means to be replaced. This may require the use of one local flow measuring device 4.X, for example one flow measuring device per injector 2, and each accumulator located between the flow measuring device 4.X and the injector (This embodiment is not shown in Figures 2.1 and 2.2, where only one local accumulator 6 per cylinder is shown).

The above embodiments are the same as the system shown in Fig. For example, the main control box 200 is also used here. The main control box 200 processes the signals from each of the injectors and does not process the cylindrical signals any more.

3 shows a variant in which all of the injectors operate simultaneously and a solenoid 1014 (associated with the associated cylinder) is connected to the same cylinder with an injector in which all the solenoids 1014 are connected in series 120). In this embodiment, the cylinder local control box 100 controls all the injectors, and a cylinder local flow measuring device and a possible accumulator are applied. This means that the system is integrated and simplified.

A variant embodiment is that one injector local control box can control the remaining injectors based on a single cylinder local flow measurement instead of the cylinder local control box 100 mentioned in FIG. As described in Figures 2.1 and 2.2, this modification will mean that one cylinder local control box is replaced by one injector local control box. Such an implementation would be substantially simpler in nature with a minimum of cables, flow meters, and the like.

In principle, you may have two or more injector local control boxes out of all, independently controlling all the injectors for one cylinder. If this is combined with the monitoring function in the active injector local control box 101, a redundancy system can be built up to take over the next injector, for example via a relay access and cable, due to an error in the previous injector. Finally, the injector local control box can trigger an alarm when the preceding injector is defective at the same time.

Figures 4.1 and 4.2 illustrate injectors that may be used in systems of the type described above. Pressurized oil is supplied to the injector 2 to the supply channel 20100 through the branch pipe 21 (see Fig. 2.1 and Fig. 3).

The injectors illustrated in Figures 4 and 5 include a nozzle 1001 installed in the inner valve housing 1006 through an outer scoop tread. The valve housing 1006 itself has a flange that partially overlies the injector housing 1017 itself and the assembly flange 1007. The injector housing 1017 is assembled to the outside of the nozzle 1001 and the assembly of the valve housing 1006, wherein the injector housing 1017 is fitted to the flange, for example, in a fitting manner. At the top, the inner valve housing 1006 is made of a flange with an O-ring groove, and the subsequent rotation will cause the valve housing 1006 to continue to the length of the solenoid core / armature housing 1009. The O-ring 1008 ensures that the pressurized fluid remains within the valve housing 1006 and the solenoid core / armature housing 1009. A main flange 1010 is provided around the solenoid core / armature housing 1009 and the main flange 1010 is coupled with the nozzle, the solenoid core / armature housing 1009 and the assembly flange 1007 through the scruff 1011 The injector housing is holding. The nozzle / valve housing assembly 1001/1006 is located within the injector housing and prevents dust and oil debris from entering deep into the injector housing 1017 by the O-ring 1002.

The solenoid core / armature housing 1009 is provided with a valve body 1003 and an armature / piston 1012 with an inner screw tread fixed by a sharpened squeeze 1013 of a tread joint. The armature 1012 has several channels 1023 for carrying pressurized oil in the direction of the nozzle. The possibility of movement of the valve body / armature (1003/1012) is determined by the cavity (20200).

In the injector 2, the oil is delivered through the cavity 20200 and the injector and channel 1023. The oil then passes to the cavity 1022 through the channel 1021 and into the cavity 1020 through which the oil is delivered to the cavity around the ball valve seat 1019 via the gap 1030. The gap is formed between the valve body stem 1003 and the wall surface 1031 in the boring that receives the valve body stem.

When the solenoid 1014 is activated, the valve body 1003 moves in the opposite direction of the solenoid 1014 until the cavity 20200 is filled by the armature / piston 1012. When the valve body 1003 integrated with the ball 1016 lifts the ball set 1019, the pressurized oil is transmitted through the valve seat 1019 via the channel 1018 and the nozzle hole 1040 It comes out through. The spring 1005 causes the injector 2 / ball set 1019 to move between the valve body 1003 and the armature / solenoid 1013 when the electromagnetic signal from the control box 100 through the line 120 from the injector solenoid 1013 is switched off. The piston 1012 is pressed in the direction opposite to the ball set 1019 so as to be sealed.

In Fig. 4, the spring 1005 is closed when the solenoid 1013 is switched off. In FIG. 4, the elastic force can be adjusted by adjusting the compression of the spring by setting the position of the nut 1004. In fact, the elastic force required to seal the valve satisfactorily and quickly can be determined by empirical experiments seeking a compromise between the solenoid force and the elastic force. So the compression can be constant and the "nut" is integrated into the valve in the form of a rest / collar that the spring is able to withstand.

When the ball seat 1019 is closed again, the pressurized oil in the supply channel 20100/20200 is actuated in the valve body 1003 to maintain both the spring 1005 and the ball seat 1019 of the injector in which the oil pressure is sealed. .

The injector valve function is performed by the ball valve body, as illustrated in Fig. It is possible to use injectors that spray and / or form oil jets, and injectors with one or more nozzle holes 1040 may be used.

 Injector control by the electronic signal 120 allows for free and independent control when opening and closing the injector / valve and thereby controlling the opening period.

Fig. 5 functionally corresponds to the system of Fig. 4 in principle. However, other variant embodiments of the injection are provided, and a pressure measurement or sample of the lubricant residue can be provided through the outlet 20000 located at the side of the flange from the cylinder. Outside the nozzle / valve housing 1001/1006, the injector has a gap with respect to the injector housing 1017 and communicates with the outlet 20000 through this gap.

1: N cylinder 2: X injector, 4: Flow measuring device, 6: Accumulator,
10: hydraulic pump device (pump facility), 11: pump, 12: filter, 13: choke valve,
14: opening / closing valve, 20: pressure valve, 21: branch portion, 22: branch pipe,
31: lubricating oil supply line (main supply part), 34: supply line, 200: main control box
100: Day tank (control box), 650: Signal cable (signal line),
1003: valve body, 1014: solenoid, 20100: supply channel,
1006: valve housing, 1001: nozzle, 1002: O-ring, 1003: valve body stem,
1005: spring, 1007: flange, 1010: main flange, 1011: squeak
1009: solenoid core / armature housing, 1012: armature / piston,
1013: Squeak, 1017: Injector housing, 1019: Ball valve seat,
1020, 1022: cavity, 1021, 1023: channel, 1030: gap, 1031:
1040: nozzle hole, 20000: outlet, 20100, 20200: supply channel, 20200: cavity.

Claims (19)

- a lubricating oil supply consisting of a pump or accumulator;
A supply line from said lubricating oil supply;
- a plurality of injectors having an inlet, an opening and closing valve device and at least one nozzle hole for injecting said cylinder lubricant into said associated cylinder, said injector being connected to said supply line and corresponding to a plurality of cylinders in an engine or multiple engines; And
A dosing system for cylinder lubricating oil in a large diesel engine cylinder comprising a control device for controlling each on-off valve device,
Wherein the dosing system comprises a flow rate measuring device for measuring the flow rate and the amount of oil actually dispensed for each injector and / or each cylinder, the flow rate measuring device being connected to a control device for application to closed circuit control And the signal line is connected to the control device for direct delivery of the load / indicator signals to the control device, in order to control the timing and dosing of one or more injectors per cylinder block, according to a reference signal from the engine, Wherein the opening and closing valve is an electromechanical valve incorporated in the injector for dispensing lubricating oil, wherein the electromechanical valve includes a spring bias valve stem, the control device comprising: And to compare the measured value with the expected / planned oil amount. A system for the administration of a cylinder lubricant for a large diesel engine cylinder. 2. The apparatus of claim 1, wherein the control device comprises a local control box for each cylinder to control timing and dosing of all injectors per each cylinder, the signal from the flow measuring device being such that the measured value is compared to the expected flow rate Wherein the local control box adjusts the opening time for the individual injectors for the cylinder in question according to the magnitude of the deviation. 3. A dosing system as claimed in claim 1 or 2, wherein from 4 to 10 injectors are used for each cylinder. 2. A dosing system according to claim 1, wherein a local pressure accumulator is provided for each injector or each injector associated with each cylinder or all injectors. The dosing system according to claim 1, wherein each injector has an outlet for connection to a return line for returning excess oil to the lubricant supply or for performing pressure measurements. 2. The valve system according to claim 1, wherein each of the injectors is made of one device, and the opening / closing valve includes a valve set that interacts with the ball valve body, and is disposed between the stem of the valve body and the wall surface of the valve guide of the opening / closing valve And a gap of 10 mu m or more in width. 2. The apparatus of claim 1, wherein the dosing system comprises a flow measuring device having the same operating range for each injector and each cylinder, the control device being connected to both of the flow measuring devices, Receiving a first signal from a measurement device and receiving a second signal from a cylinder center flow meter, wherein the first signal is associated with more flow than the second signal. 2. The apparatus of claim 1, wherein the dosing system includes a flow measuring device having a different operating range for each injector and each cylinder, the flow measuring device having a narrow operating range includes a local flow measurement And the flow measuring device having a wide operating range is a cylinder-based flow rate measuring device. 2. A dosing system as claimed in claim 1, wherein the dosing system comprises one cylinder center flow meter coupled to at least one local flow meter connected to the injector. 2. A dosing system according to claim 1, wherein the dosing system comprises a combination of a cylinder local flow measurement device and an injector local flow switch. - pressurizing the lubricating oil at a lubricating oil supply which may consist of a pump facility or an accumulator;
- transferring lubricant from the lubricant supply through the supply line;
- injecting lubricant into the associated cylinder through a plurality of injectors having an inlet, an on-off valve and one or more nozzle holes by connecting said supply line with an injector; And
- controlling each on-off valve device with a control device, wherein in the method of administering the cylinder lubricating oil to a large diesel engine cylinder,
The result of the flow rate measurement is transmitted to the control device by measuring the central flow rate of each cylinder for the actual amount of oil injected per unit injectors and / or by measuring the local flow rate for each injector, To the control device in order to control the timing and dosing of one or more injectors per cylinder in accordance with a reference signal from the engine, And controlling the timing and oil amount within a required range by transferring a control signal to the on-off valve device, wherein the injection of the lubricating oil is carried out by injecting the lubricating oil into the injector Operated by an electromechanical valve-type on-off valve incorporated in Wherein the cylinder lubricant is fed to a large diesel engine cylinder. 12. The method of claim 11, wherein the injector local flow measurement is performed in combination with a central flow rate measurement per cylinder. 13. The method of claim 11 or 12, wherein the supply pressure at the feed line is monitored. 14. The method of claim 13, wherein the feed pressure in the feed line is used as a mediator to control the dosage. 12. The method of claim 11, wherein the timing and dosage are regulated by the opening and closing time of the electromechanical valve. 12. The method of claim 11, wherein the method is set with a flow measuring device having the same operating range for each of the injectors and each cylinder, the control device being connected to both of the flow measuring devices, Characterized in that the flow rate from the first measured value is selected from a first measured value from the local flow measuring device in the injector and from a second measured value from the cylinder center flow measurement, A method of administering a cylinder lubricant. The flow meter according to claim 11, wherein a flow measuring device having a different operating range is set for each injector and each cylinder, a flow measuring device with a narrow operating range is selected as a local flow measuring device connected to the injector, Wherein the wide flow rate measuring device is selected as the cylinder center flow rate measuring device. 12. The method of claim 11, wherein only one cylinder center flow measurement is performed and combined with at least one local flow measurement in the injector. 12. The method of claim 11, wherein the flow rate measurement is performed by combining a cylinder local flow rate measurement and a cylinder flow rate measurement device, and combining the injector local flow rate registration and the injector local flow rate switch.

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