KR100411409B1 - Cylinder Lubrication System for Multi-cylinder Internal Combustion Engine and Lubricant Flow Rate Control Method Therefrom - Google Patents

Abstract

The cylinder for a multicylinder internal combustion engine is provided with the piston which the piston ring slides on the inner surface of the cylinder liner, and reciprocates in each cylinder 1. The cylinder lubricator 3 measures the lubricating oil by a plurality of dosing pistons 53 movable longitudinally in the dosing cylinder 42 and supplies it to the plurality of lubrication points 2 formed on the inner side of the liner. The plurality of dosing pistons 53 are mounted to the actuator pistons 44, 44a, 44b, the actuator piston is inserted into a hydraulic cylinder having a hydraulic chamber 45, the hydraulic chamber is a hydraulic fluid actuator piston And the dosing piston may be connected to the pressure source or the drain by the dosing piston 37 to carry out a delivery stroke for supplying lubricating oil to the lubrication point by moving the dosing piston thereof in the longitudinal direction.

Description

Cylinder Lubrication System for Multi-cylinder Internal Combustion Engine and Lubricant Discharge Rate Control Method

The present invention relates to a lubrication device for a multi-cylinder internal combustion engine having a piston ring in each cylinder, the piston ring sliding on the inner surface of the cylinder liner, the lubrication device is a plurality of lubrication points formed on the inner surface of the cylinder liner The lubricating oil metered in is supplied by a plurality of dosing pistons movable longitudinally in the associated dosing cylinder.

Such a cylinder lubricator is known from German patent Al-28 27 626, in which the dosing pistons are mounted in a row arranged on the bottom of the lubricating oil container, the container being provided with a rotary arm having a lower end opposite the corresponding piston. And a shaft supported by each piston. On the opposite side of the top of each swivel arm is provided a set screw which limits the rotation of the swivel arm. By adjusting the fixing screw, the starting position and stroke of the piston are determined. The piston is driven to reciprocate by a rotating camshaft journaled to the lubricant container, the cam acting on the side of the lower end of the rotating arm facing away from the dosing piston. The camshaft rotates in synchronism with the crankshaft of the engine and allows a supply stroke of one stroke per revolution of the engine crankshaft for each engine cycle. If it is not necessary to supply the maximum amount of lubricating oil in each stroke of the dosing piston in the operating mode of the engine, the cam shaft of the camshaft causes the rotatable stop member to come into contact with the top of the rotating arm so that the dosing piston no longer returns to its starting position. It is possible to prevent the supply of lubricant during subsequent operations.

This type of lubrication device consists of many mechanical parts, and the dosing piston can be operated only when the cam of the camshaft which rotates in synchronism with the crankshaft of the engine is slow to operate. Moreover, there is a disadvantage that a mechanical driving force transmission means is required between the camshaft and the crankshaft of the lubricator. In addition, since the dosing cylinder is filled with lubricating oil through a non-return valve, the filling of the dosing cylinder is affected by the viscosity of the lubricating oil. Therefore, it was usually considered necessary to heat the lubricating oil of the lubricator so that the required amount of lubricating oil supply, as far as possible, was independent of the lubricating oil inlet temperature and its quality.

A German lubricator brand lubricator is connected via a two-position, four-port switching valve to a pressure source with a feeder with two pistons with different cross-sectional areas in the cylinder. A high hydraulic pressure of about 70 bar acts on one end of the piston to actuate the piston, and when a small area piston requires a large amount of lubricating oil in normal operation, the other large piston is It works instead of a piston. The two ends of the actuating piston are alternately connected with a pressure source or a drain to carry out a lubricating oil delivery stroke. The delivery pressure is equal to the supply pressure, and the transition from one position to another occurs when the amount of delivery changes. The lubrication device has the disadvantage that two dosing pistons should be used for each lubrication point and the supply pressure to the lubricating oil point must be equal to the delivery pressure. Movement of the dosing piston can be changed to change the amount of output of the lubricator, but only when the engine is stationary.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems of the prior art, and an object of the present invention is to provide a highly reliable lubrication device which is driven mechanically independently of an engine crankshaft and supplies the required amount of lubricating oil accurately and quickly. .

1 is a schematic configuration diagram of a cylinder lubricating oil system for an internal combustion engine,

FIG. 2 is a schematic longitudinal sectional view of the pressure control device of the lubricating oil system of FIG. 1,

3 is a longitudinal sectional view of a first embodiment of a cylinder lubricator according to the present invention,

4 and 5 are longitudinal cross-sectional views of the second and third embodiments of the cylinder lubricator according to the present invention, respectively,

FIG. 6 is a plan view of the piston support yoke seen from the cross section taken along line VI-VI of FIG. 4. FIG.

Explanation of symbols on the main parts of the drawings

DESCRIPTION OF SYMBOLS 1 Cylinder 2 Lubrication point 3 Cylinder lubrication apparatus 37 Control valve

42: dosing cylinder 44, 44a, 44b: actuator piston 45: chamber

53: dosing piston

In order to achieve the above object, the cylinder lubrication device of the present invention has a plurality of dosing pistons mounted to the actuator piston, the actuator piston is inserted into a hydraulic cylinder having a hydraulic chamber, and the hydraulic fluid to the actuator piston and its dosing piston. The hydraulic chamber may be connected to a pressure source or a drain by a control valve so that the dosing piston performs a delivery stroke that moves in a direction to supply lubricant to the lubrication point. Such a cylinder lubricator can greatly simplify the structure of the lubricator by avoiding the use of rotatable shafts with corresponding shaft drives, while the dosing piston is driven mechanically independently of the engine crankshaft. The dosing piston is mounted on the actuator piston and thereby has the advantage of being able to reciprocate. Compared with the cylinder lubricator used in the prior art, reliability is improved in that a single actuator piston for operating all the dosing pistons of the lubricator without rotating parts is used instead of using the rotary cam for each dosing piston. Furthermore, instead of having a drive for every dosing piston in the drive, the present invention has one common drive. Compared to a gel-type lubricator, the lubricator according to the invention uses only one dosing piston per lubrication point, and the structure is considerably simplified in that a common actuator piston drives all the dosing pistons of the lubricator. .

It is preferred that the cross sectional area of the actuator piston of the hydraulic cylinder is considerably larger than the sum of the cross sectional areas of the dosing piston of the dosing cylinder concerned. In the drive section, the relatively large area of the actuator piston makes it possible to generate a delivery pressure which is greater than the cylinder pressure at the lubrication point upon the introduction of lubricating oil into the cylinder at the desired low pressure of the drive hydraulic fluid. In particular, in a preferred embodiment the cross sectional area of the actuator piston is at least 4 times, preferably 6-15 times larger than the sum of the cross sectional areas of the dosing piston. With such an area ratio, for example, if the driving pressure of the hydraulic fluid is 10 bar or less, the delivery pressure is 80 bar or more. This low drive pressure is realized by the preferred delivery pump which consumes less energy. Low hydraulic pressure also ensures that the pressure device of the delivery side conduit does not become too large.

The control valve can be controlled electronically by a control signal received from the engine or cylinder control device. Electronically actuated valves are components of fast acting standards, such as solenoid valves that can be directly controlled by an electronic controller capable of controlling other cylinder components. When the actuator piston receives an elastic force by the spring toward the starting position of the piston with respect to the actuator piston, the valve preferably has a three-port two-position, with the influence of the hydraulic pressure on the piston surface facing away from the starting position. Upon return to the starting position, the valve may have a four port two position.

It is desired that the cylinder lubricator can be switched to deliver a greater amount of lubricant under certain operating conditions of the engine. An improved embodiment of the present invention wherein the actuator piston is divided into a main piston and an auxiliary piston, and forms an auxiliary hydraulic chamber between the main piston and the auxiliary piston, in a simple manner. The piston is mounted on the auxiliary piston, and the auxiliary piston is movable together with the main piston from the starting position to an intermediate position where the forward movement of the main piston is prevented by the stop member, and the auxiliary piston has a predetermined operating pressure. It is characterized in that it is configured to move forward from the intermediate position when exceeding. When the cylinder lubricator attempts to deliver a relatively small amount of lubricating oil, the hydraulic pressure is kept below the working pressure of the auxiliary piston. In this mode of operation, the actuator piston moves the dosing piston each time by a distance corresponding to the distance from the starting position to the intermediate position. When a larger amount of lubricant is supplied to the cylinder liner in the operating state of the engine, such as a change in engine load, the hydraulic pressure is increased above this operating pressure. When the lubrication device is operated and the movement of the main piston is stopped by the stop member, the hydraulic pressure of the hydraulic fluid inlet side of the lubrication device and the hydraulic pressure of the auxiliary hydraulic chamber are greater than the operating pressure for the auxiliary piston, so that the auxiliary piston is the dosing piston. Is driven forward, thereby increasing the amount of lubricant supplied in each operation of the lubricator.

The cylinder lubricator has an inner chamber in communication with the lubricating oil source, each dosing cylinder is located in front of the front end face of the piston and has an inlet channel connecting the inner chamber and the dosing cylinder when the actuator piston is in its starting position. The lubricating oil delivery from the dosing cylinder is initiated when the piston blocks through the inlet channel. In such a lubrication device the dosing piston controls the opening and closing of the inlet channel so that the channel can be formed as simply an open bore without any backflow check valve. This provides the advantage that the amount of lubricating oil discharged from the dosing cylinder is independent of the viscosity of the lubricating oil, since the amount of lubricating oil in front of the dosing piston is constant regardless of its viscosity conditions at the moment the inlet channel is completely blocked by the dosing piston. to be. Before each delivery stroke, the dosing piston should be placed in a starting position where the inlet channel is not at least partially closed. After the delivery stroke of the lubricating oil is finished, the dosing piston is returned to its starting position, and during the return movement, vacuum is generated in the dosing cylinder in front of the dosing piston. When the inlet channel is not closed, the dosing cylinder is quickly filled with lubricating oil flowing from the inner chamber through the inlet channel so that the vacuum is removed at the same time as the vacuum is generated. The vacuum condition facilitates the filling of the cylinder, which is also an advantage of this embodiment.

In particular, in a simple embodiment the hydraulic fluid is lubricating oil, the inner chamber is connected to the drain port for the hydraulic fluid, the pressure of the lubricating oil at the drain port is higher than the atmospheric pressure outside the lubricator. As lubricating oil is used as the lubricating fluid, the cylinder lubricator must be connected to one conduit. The inner chamber is filled with a relatively low pressure lubricant in the drain port, and the actuator piston need not be blocked for this pressure, which is significantly lower than the lubricant delivery pressure to the lubricator. In addition, there is an advantage that a part of the lubricating oil used to drive the actuator piston flows into the inner chamber and is used in the dosing cylinder, and the amount of lubricating oil conveyed from the lubricating device is as small as possible.

The amount of lubricating oil supplied to the lubrication point by one lubrication device is individually adjustable so that the lubricant consumption can be finely adjusted and can also be minimized. To this end, the dosing cylinder can be mounted to the lubricator to enable individual length adjustment of the mounting position, and the dosing piston can be mounted to the actuator piston to enable individual adjustment of the distance between its front end and the actuator piston.

The present invention relates to a method for controlling the amount of lubricant oil discharged from a cylinder lubricator. The method uses a hydraulically driven actuator piston to simultaneously move longitudinally the plurality of dosing pistons mounted on the actuator piston, and the lubricator is operated at least one predetermined moment during the engine cycle of the associated cylinder so that the actuator piston is connected to the dosing piston. By being moved at least a predetermined distance in the longitudinal direction, the base supply of lubricant is delivered from the respective dosing piston to the associated lubrication point of the cylinder, the lubricator being selectively controllable while the engine is running so that the lubricant is more than the base supply It is characterized in that is sent to each lubrication point.

The use of the actuator piston for the movement of a plurality of dosing pistons has the advantage that the lubricator moves quickly and is simple but very reliable. Lubricant when the piston of the engine cylinder is at the opposite side of the lubrication point, for example when the piston ring part of the cylinder piston is at the opposite side of the lubricated lubrication point, due to the lubricator operating at a given moment in the engine cycle. Is supplied. The fact that the actuator piston supplies a certain amount of lubricant to each lubrication point as it moves forward, and that the lubrication system can be selectively controlled to supply more lubricant, is a necessity of lubrication raised when lubricating cylinders of internal combustion engines. Conforms to That is, during normal operation at constant engine load, cylinder lubrication is made in a relatively small amount, usually proportional to the engine load, while a larger amount of lubricant can be supplied at varying loads or under abnormal engine operating conditions. have.

In an operating mode where the need for engine lubrication is low, the basic supply of lubricating oil during one engine cycle should correspond to the amount of lubrication delivered to the lubrication point. Since the oil pressure of the pressure source in communication with the hydraulic chamber of the actuator piston is increased by exceeding the predetermined operating pressure, more lubricant is supplied from the lubricator. By operating the lubricator by the method of the present invention, when a smaller or larger amount of lubricating oil is to be supplied, the required amount of lubricating oil is sent out by operating the actuator piston once. This makes it possible to simply and preferably control the lubricator. Moreover, according to the method of the present invention, a single lubricator can be used for lubrication of a plurality of cylinders or for lubrication of the same cylinder at more lubrication points than the dosing piston of the lubricator. This is because the discharge side of the lubricator is equipped with a number of switching valves that connect the lubricator to the lubrication point where the lubricating oil must be supplied in the current operating state of the actuator piston. A lubricator running quickly at a part of the engine cycle can deliver lubricant to the first set of lubrication points connected, so that the switching valve connects the lubricator to the other set of lubrication points and thereby activates the actuator piston. .

In the method according to a variant of the invention, the basic supply of lubricating oil is less than the amount of delivery to the lubrication point made during one engine cycle, and the actuator piston is operated to perform several reciprocating strokes during one engine cycle, More actuators are supplied by operating the actuator more times during one engine cycle. The fast acting lubricator can be operated several times during one engine cycle, thereby selecting a base supply per unit motion less than the lowest lubricating oil to be delivered during one stroke of the reciprocating piston of the engine cylinder, It is possible to operate the actuator piston a number of times to provide a total delivery amount corresponding to lubrication. Thus, highly accurate lubrication is possible under all operating conditions and is easily controlled by the electronic controller to operate the lubricator as many times as necessary.

The reciprocating stroke at the maximum stroke of the actuator piston is preferably carried out in less than 60 ms, more preferably in less than 40 ms. Since the full engine cycle of a large two-stroke crosshead engine is typically 0.25-1 s, the cylinder lubricator can be operated at least 3-16 times, preferably 6-25 times, during one engine cycle. With such a fast acting lubricator, lubrication can be carried out with a very accurate amount and very precise timing with respect to the piston position of the cylinder. It is also possible to lubricate a plurality of cylinders using the same lubricator or to lubricate several levels in one cylinder. In addition, the lubricator operates quickly enough to carry out the correct lubrication of the cylinders of the four-stroke engine, and can carry out the entire engine cycle for example for 0.6-0.1 s.

Hereinafter, with reference to the accompanying drawings showing an embodiment of the present invention will be described in detail the present invention.

1 shows a configuration of a cylinder lubricating oil system for a two-stroke crosshead engine that is a fixed power generating engine or a ship propulsion engine. The engine is a multicylinder engine, and only two engine cylinders 1 are shown in the figure for clarity. The inner diameter of the cylinder liner is typically in the range of 25 cm to 100 cm, and the piston reciprocating in the liner typically runs at a stroke distance in the range of 90 cm to 300 cm, with three to five slides on the inner side of the liner. A piston ring for a pressure seal is provided. Cylinder lubrication is for maintaining a lubricating oil film on the inner side of the cylinder liner so that the friction between the inner side of the liner and the piston ring is kept moderately low.

Each cylinder liner has a plurality of lubrication points to which lubricant is supplied to the inner side of the liner by one or more cylinder lubricators 3. The supply conduit 4 to each oil supply point is equipped with a non-return valve 5 such as a check valve near the hole of the liner such that the cylinder pressure does not act as a supply conduit when the lubricant is not refueled. For distribution of the lubricating oil in the circumferential direction of the liner, a plurality, for example two to five or more lubrication points, are evenly distributed in rows in the circumferential direction of the liner. The liner may have such a plurality of rows of refueling points disposed at different levels in the longitudinal direction thereof. The lubricator 3 supplies lubricating oil to all lubrication points of the associated cylinders, each cylinder having two or more lubricators for lubricating the heat of each lubricating point, or the discharge side of the lubricator. One lubricator may supply lubricating oil to the lubricating points of the plurality of cylinders when it is provided with one or more switching valves in alternating communication with the lubricating points of each of the relevant cylinders.

Lubricant consumption for cylinder lubrication in normal engine operation ranges from 0.4 g / kWh to 0,9 g / kWh, typically 0.6 g / kWh. Cylinder maximum power is, for example, in the range of 400 kW to 5800 kW and typically requires 240 g / h to 3480 g / h of lubricant per cylinder.

The cylinder lubricator 3 is a pressure source for hydraulic fluid in the form of a pressure conduit 6 connected to a delivery conduit 7 from two engine or motor driven pressure pumps 8, one of which is a working pump and the other of which is a reserve pump. And it is connected to the hydraulic fluid drain pipe of the conveyance conduit 9 form which conveys excess supply lubricating oil to the tank 10. FIG. The tank 10 has a discharge tube 11 and a filling conduit 12. On the inlet side, two pumps 8 are connected in parallel with the supply conduits 13 from the tank 10, and the supply conduits in front of each pump are provided with a shutoff valve 14 and a filter 15, The filter has a somewhat coarse mesh size of 100 μm to 200 μm. The pressure pump 8 is connected in parallel with the pressure conduit 6 via a respective non-return valve 16 on the delivery side and with a microfilter 17 of 10-50 μm mesh size to ensure proper purity of the lubricant. . The pump 8 and its associated valve 14 are controlled by an electronic controller 18, which is controlled by the pressure in the pressure conduit 6 or by a plurality of unshown figures, as described below. The flow meter can be used to monitor the operating state of the pump. If the actuating pump fails, the electronic control 18 switches the two valves 14 and initializes the reserve pump. The accumulator 19 equalizes all pressure pulses occurring in the pressure conduit 6 when the lubricator 3 is operating.

The pump 8 discharges the lubricating oil at a pressure exceeding the maximum pressure required at the inlet of the cylinder lubricator 3. The pressure in the pressure conduit 6 is always adjusted down to the required level by the pressure control device 20, and the pressure control device 20 drains some lubricating oil into the conveying conduit 9 according to the required pressure. .

The pressure control device is shown in more detail in FIG. 2 and communicates with the pressure conduit 6 and the conveying conduit 9 at two ports 21 and 22, respectively. The pressure transducer 23 continuously measures the pressure in the pressure conduit 6 and transmits a signal thereto through the signal line 24 to the electronic controller 18. For example, a two-position three-port control valve 25, such as a solenoid type magnetic valve, opens the pressure control valve 26 or at an adjustable predetermined minimum pressure that opens the port 21 at an adjustable maximum predetermined pressure. It is in communication with any one of the pressure control valve 27. The pressure is set corresponding to the maximum pressure and the minimum pressure required in the pressure conduit 6. Taking the available pressure as an example, the pressure control valve 26 may open at a pressure of 20 bar, and the pressure control valve 27 may open at a pressure of 5 bar. The discharge side of the pressure control valves 26 and 27 communicates with the port 22. The control valve 25 receives a control signal from the electronic control device 18 through the wire 28.

The pressure in the pressure conduit 6 can be controlled to the required level of pressure between the maximum and minimum pressure by switching the control valve 25 between the two positions at an appropriate switching ratio. When the pressure control valve 26 is in communication with the pressure conduit 6, the pressure in the pressure conduit rises close to the maximum pressure, and when the pressure control valve 27 is in communication with the pressure conduit 6 of the pressure conduit 6 The pressure is close to the minimum pressure. This is a pressure regulating operation periodically controlled by the electronic controller 18 by the control valve 25. Preferably, for safety of the internal combustion engine, the control valve 25 is in a position where the port 21 is in communication with the pressure control valve 26 when no magnetization current flows through the wire 28. If any element of the electromagnetic pressure control device fails, the pressure in the pressure conduit 6 is set to the maximum pressure.

The pressure control device of the above type controls the pressure and instead of using a pump having a fixed discharge flow rate, the pump can control the pressure in the pressure conduit 6 with the discharge flow rate. Instead, the pressure controller may be a variable valve that sets the pressure in accordance with the voltage level received from the controller.

The electronic controller 18 is connected to a power source by wires 29 and receives information about the current operating state of the engine via a plurality of wires 30-32. Such information can be, for example, a signal for the engine load provided by the wire 30 and a signal from the engine governor, a signal for the rotational movement of the crankshaft provided by the wire 31, and the wire 32 Signal lights for special operating conditions where one or more engine cylinders need to be lubricated with increased lubrication. The signal for the rotational movement of the crankshaft can be obtained, for example, from a so-called incremental encoder, and can contain information on the current angular position of the crankshaft.

The control device furthermore receives information from the pressure transducer 23 about the current pressure of the pressure conduit 6. Through the wires 33, 34 and the wires to the valve 14, not shown, the electronic control device 18 is controlled through the wire 28 by the pressure pump 8. The control device is connected to the control valve 37 of each lubricator 3 via wires 35 and 36. If the control detects an abnormal operating condition, an alarm is triggered through the wire 38. For safety reasons, the pressure transducer and other possible elements of the lubricator are doubled by one or more of the same type of spare element in case one element fails.

The operation monitoring process by the control device for cylinder lubrication includes the process of confirming detection by the pressure transducer against pressure fluctuations in the pressure conduit 6 and immediately providing an operation signal to the control valve 37 thereto. . This pressure fluctuation shows that the relevant lubricator performs a dosing stroke to supply lubricant from the pressure conduit 6. If pressure fluctuations are to be expected, the control will generate an alarm for the possibility of a fault in the cylinder lubricator.

An example of a cylinder lubricator 3 is shown in FIG. 3. The control valve 37 is mounted to the casing 39, the casing comprising a first portion 39a having a connecting portion 40 for the pressure conduit 6 and a connecting portion 41 for the conveying conduit 9. And a connection 43 for each supply conduit 4 which supplies oil from the dosing cylinder to the lubrication point at the same time. The first part and the second part of the casing are joined by bolts (not shown) which are inserted from the cover side and screwed into the holes of the bottom face of which the screw of the first part 39a is formed.

The actuator piston 44 is inserted into the bore of the first portion 39a to act as a hydraulic cylinder, and the end face and the bore of the piston communicate with the discharge port 47 of the control valve via the channel 46 ( 45). The axis of symmetry of the piston extends parallel to the longitudinal axis of the dosing cylinder. The control valve 37 is further provided with an inlet port 48 in continuous communication with the pressure conduit 6 and a drain port 49 in continuous communication with the conveying conduit 9. The valve slide 50 moves in two positions, that is, between the position shown in the drawing in which the drain port 49 and the discharge port 47 are in communication, and the position in which the discharge port is in communication with the inlet port 48. When the coil 52 'is magnetized, the valve slide is moved to block the drain port 49.

On the outside of the hydraulic cylinder, the piston 44 is provided with a radially protruding collar portion 52 serving as a yoke on which the dosing piston 53 is mounted. The dosing piston has two protruding collars at its ends, and the protruding collars push the assembled dosing pistons into the grooves 54 which are opened out of the piston collar portion 52 to form the piston collar portion 52. Holding both sides, FIG. 6 shows a state in which one piston 53 has been removed to show the corresponding groove 54. In this assembly process, the dosing piston is fixed so as not to be displaced in the longitudinal direction from the actuator piston, but fine adjustment in the radial and circumferential directions is possible so that the dosing piston is sufficiently coaxial with the dosing cylinder 42.

The casing 39 has an inner chamber 55, which is in communication with the connector 56 for the conveying conduit through the hole 56 of the actuator piston and the channel 57 so as to allow continuous flow. The pressure of the lubricating oil filled in the inner chamber is maintained for example between 1 and 3 bar. The chamber 55 has an annular groove 58 traversing the dosing cylinder so that each cylinder has a feed channel connecting the chamber 55 and the dosing cylinder when the dosing piston is in the starting position shown in the figure. Provide easily. Optionally, each bore may be provided with a bore constituting the channel.

Each dosing cylinder is provided with a non-return valve in the form of a spring loaded ball 59 at the discharge end such that the lubricant can only be discharged from the cylinder.

The stop member 60 determines the stroke of the actuator piston at each stroke, which is achieved by the front end of the piston hitting the end face of the stop member. The compression spring 61 previously acts on the actuator piston in the direction toward the starting position and contacts the stop member against the adjusting screw 62 fastened to the screw hole of the end 39c, depending on the degree of tightening the adjusting screw. This limits the stroke of and therefore the amount of lubricant delivered by the dosing piston per stroke. The adjusting screw may be provided with a scale showing the relationship between the amount of lubricating oil delivered and the adjusting of the screw.

When the controller generates a signal to activate the lubricator, the coil 52 'is magnetized and the valve slide 50 communicates the pressure conduit 6 and the hydraulic chamber so that pressurized lubricant flows into the chamber 45. To move the actuator piston and its dosing piston to the left in the drawing. The front end face of the dosing piston passes through the inlet channel and blocks it during initial movement, at which time lubricant is delivered to the lubrication point. When the actuator piston comes in contact with the stop member 60, the transfer of lubricating oil is stopped. At this time, the valve slide 50 is switched to connect the connecting portion 41 to the conveying conduit 9 with the hydraulic chamber 45, so that the lubricating oil in the chamber is pressurized and discharged and the actuator piston is returned to its starting position by the spring 61. do. In the return movement of the dosing piston, a vacuum is generated in the dosing cylinder 42 until the piston end opens the inlet channel and the lubricant from the inner chamber flows into the cylinder.

In the following description of the modification, the same reference numerals are used for elements having the same function, and only the other parts will be described with respect to the first embodiment.

4 shows an embodiment in which the actuator piston is divided into a main piston 44a and an auxiliary piston 44b. The main piston is inserted into the bore of the auxiliary piston so that the piston has an annular auxiliary hydraulic chamber 63 therebetween. The chamber 63 is in continuous communication with the chamber 45 through the longitudinal channel 64 of the main piston. The main piston 44a is provided with the center member 65 which penetrates the end wall of the auxiliary piston. The annular collar portion 52 of the actuator piston is mounted to the auxiliary piston 44b so that the dosing piston operates according to the movement of the auxiliary piston.

When the control valve 37 is actuated, the pressurized lubricating oil enters the hydraulic chambers 45 and 63 and the two pistons move substantially longitudinally together towards the left side in the figure. When the end face of the center member 65 comes into contact with the stop member 60, forward movement of the main piston 44a is inhibited. During such movement, the auxiliary piston is brought to an intermediate position, in which the auxiliary piston is the pressure between the lubricating oil pressure of the conveying conduit 9 and the pressure conduit 6 in the annular region forming the end wall of the hydraulic chamber 63. It receives the force generated by the car and the compressive force of the spring 61.

If the pressure in the pressure conduit 6 is less than a predetermined operating pressure such that the elastic force of the spring acting on the auxiliary piston in the intermediate position and the force in the annular region are equal, the auxiliary piston is moved forward from its intermediate position. You will no longer be able to move.

If the pressure in the pressure conduit 6 is greater than the operating pressure, the pressure at the end face overcomes the elastic force of the spring so that the forward movement of the auxiliary piston continues even after the movement of the main piston is inhibited. The compression force by the spring 61 is increased according to the degree to which the spring is compressed. Therefore, the so-called end pressure, which is a pressure greater than the operating pressure for moving the auxiliary piston to always come in contact with the shoulder 66 of the second part 39b, is required in the chamber 63. By controlling the pressure in the pressure conduit 6 so as to be a value between the operating pressure and the end pressure, the supply amount of the lubricating oil is adjusted to the maximum supply amount obtained by the movement of the auxiliary piston so as to always contact the jaw 66 and the movement to the intermediate position. Can be adjusted by means of a slide scale between the basic feeds delivered.

The actuator piston 44 of the first embodiment shown in FIG. 3 is moved against the elastic force of the spring, and the adjustment of the supply amount of the lubricating oil can be performed by the pressure control of the pressure conduit 6. However, the embodiment shown in FIG. 4 has an advantage that a precise pressure control is possible because the annular area of the auxiliary piston is considerably smaller than the entire area of the actuator piston, so that a larger pressure change is required to change the supply amount of the lubricating oil.

In the second embodiment, between the end 39c of the casing and the second part 39b, a casing 39d is inserted in which a flow meter is provided opposite the outlet of each dosing cylinder. The flow meter includes a ball 67 mounted to the spring, which moves away from the starting position shown when the lubricant is discharged from the cylinder. The movement of the ball 67 as described above operates a signal generator for outputting an operation signal to the electronic control device 18. The flow meter allows the lubricating oil to be sent to each lubrication point.

5 is different from the above-described embodiment in the following points. In other words, the supply of lubricating oil to the dosing cylinder is supplied from the chamber 69 surrounding the second portion 39b of the casing and through the inlet channel 68. The inlet channel is provided with a non-return valve 70. This embodiment is particularly useful when a fluid other than lubricating oil is used as the hydraulic fluid such as dilute hydraulic oil.

The details of the embodiments described above can be combined to create a new embodiment, so that the flow meter can be adopted as any option to the basic design specification shown. In addition, various modifications may be made to the elements shown in the drawings within the scope of the present invention. For example, instead of using a mechanical spring 61, an air spring or hydraulic return means may be used. Moreover, the control valve may be driven mechanically or pneumatically instead of electronically as shown. If the hydraulic fluid is not lubricating oil, an inner oil-filled chamber is used but connected to an independent lubricating oil source, and the hydraulic channel 57 is no longer needed.

Claims (12)

A plurality of lubrication formed on the inner side of the liner by metering the lubricating oil by the reciprocating piston, which piston ring slides on the inner side of the cylinder liner, and a plurality of dosing pistons movable longitudinally in the dosing cylinder 42. In the cylinder lubricator 3 for a multi-cylinder internal combustion engine provided with a lubrication device for supplying the point 2 to each cylinder 1, a plurality of dosing pistons 53 are connected to the actuator pistons 44 (44a, 44b). And an actuator piston is inserted into a hydraulic cylinder having a hydraulic chamber 45, which is connected to a pressure source or a drain of the hydraulic fluid through a control valve 37 to connect the actuator piston and its dosing. A cylinder lubrication field, characterized in that the dosing piston performs a delivery stroke for supplying lubricating oil to the lubrication point by moving the piston in the longitudinal direction. . A cylinder lubricator as claimed in claim 1, wherein the cross sectional area of the actuator piston (44, 44 a) of the hydraulic cylinder is larger than the sum of the cross sectional areas of the dosing piston (53) of the associated dosing cylinder (42). 3. A cylinder lubrication device according to claim 2, wherein the cross sectional area of the actuator piston is at least 4 times, preferably 6-15 times larger than the sum of the cross sectional areas of the dosing piston. 2. The cylinder lubrication device according to claim 1, wherein the control valve (37) is a three-port two-position valve operated by a control signal received from an engine or cylinder control device (18). 2. The actuator piston is divided into a main piston 44a and an auxiliary piston 44b, and forms an auxiliary hydraulic chamber 63 between the main piston and the auxiliary piston, and the dosing piston is connected to the auxiliary piston. The auxiliary piston moves together with the main piston from the starting position to an intermediate position where the forward movement of the main piston is prevented by the stop member 60, and the auxiliary piston has a pressure in which the pressure of the auxiliary hydraulic chamber exceeds a predetermined operating pressure. When the cylinder lubricating device, characterized in that moving forward from the intermediate position. 6. The lubrication device (3) according to any one of the preceding claims, wherein the lubrication device (3) has an inner chamber (55) connected to a lubricating oil source, each dosing cylinder (58) located in front of the front face of the piston (53). A cylinder lubricating device, comprising: connecting the inner chamber and the dosing cylinder when the actuator piston is in the starting position; . 7. The hydraulic fluid according to claim 6, wherein the hydraulic fluid is lubricating oil, and the inner chamber 55 is connected to the drain port 49 for the hydraulic fluid, and the lubricating oil pressure of the drain port is greater than the atmospheric pressure outside the lubricator 3. Cylinder lubricator. 6. The dosing cylinder according to any one of the preceding claims, wherein the dosing cylinder can be mounted to the lubricator to enable individual length adjustment of the mounting position, the dosing piston having its front end and the actuator pistons 44, 44a, 44b. A cylinder lubricator, characterized in that it is mounted to the actuator piston to enable individual adjustment of the distance between them. In the method of controlling the amount of lubricating oil discharged from the cylinder lubricator 3, a hydraulically driven actuator piston is used to simultaneously longitudinally move a plurality of dosing pistons 53 mounted on the actuator pistons 44, 44a and 44b. The lubrication device is operated at least one predetermined moment in the engine cycle of the associated cylinder 1 such that the actuator piston is moved at least a predetermined distance in the longitudinal direction of the dosing piston so that the basic supply amount of the lubricating oil is applied to each dosing piston 53. Is delivered to the associated lubrication point of the cylinder, and the lubricator is selectively controllable while the engine is running so that more lubricating oil is delivered to each lubrication point than the basic supply. 10. The dosing piston according to claim 9, wherein the basic supply amount of lubricating oil for one engine cycle in an operating mode in which the engine is not required for lubrication corresponds to a delivery amount to a lubrication point, and the dosing piston in an operating mode in which a larger amount of lubricating oil is required in the engine. Since the hydraulic pressure of the pressure source in communication with the hydraulic chambers 45 (45, 63) of the actuator piston is increased beyond the predetermined operating pressure by moving the 53 over a predetermined distance, more lubricating oil is supplied from the lubricator. Control method characterized in that. 10. The base supply of lubricating oil as set forth in claim 9 is less than the amount of delivery to the lubrication point during one engine cycle, and the actuator pistons (44, 44a, 44b) perform several reciprocating strokes during one engine cycle. Control, characterized in that the lubricating oil is supplied by operating the actuator more times in one engine cycle. 12. The reciprocating stroke at the maximum stroke of the actuator pistons 44, 44a, 44b is carried out in less than 60 ms, more preferably in less than 40 ms. Control method.

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