DK169589B1 - Central lubricator for oil supply of lubrication points on a large diesel engine cylinder - Google Patents

Description

in DK 169589 B1

BACKGROUND OF THE INVENTION The present invention relates to a central lubricator assembly for oil supply of lubrication points on a large diesel engine cylinder and of the type containing a plurality of parallel piston pumps actuated by individual actuators moved back and forth by cooperating with drive shafts on a common rotary drive shaft and individually adjustable for adjusting the stroke of the individual pumps by means of respective set screws arranged in screw holes on a common support part, which assembly is further of the type provided with control means for collective graduated change of the actuating means. setting.

The piston pumps suck oil from a common tank and deliver the oil to the associated different lubrication points on the engine cylinder, where the lubrication pulses should appear just as the respective lubrication points are passed by the piston rings on the motor piston. The drive shaft is rotated synchronously with the main shaft of the engine, and the various drive shafts 20 project in different directions from it, precisely so that the lubrication points are operated at the correct times according to their location in the axial direction of the cylinder.

It is generally desirable that an individual adjustment of the oil supply to the individual lubrication points can be performed, which is obtainable by using the said set screws. The drive lugs can push the pump pistons to a fixed bottom position from an advanced starting position which may be more or less advanced depending on the setting of the associated set screws. However, such an adjustment is usually performed only during the assembly or run-in of the lubricator itself, after which the settings are only occasionally adjusted during the life of the engine.

35 It is not usual to use other or additional devices to regulate the lubricating oil flow to the lubrication sites, but it has been previously suggested that, under various special operating conditions, an additional, collective regulation may be used, whereby the lubricator is completely switched off either permanently for a shorter or longer period or in an intermittent manner, e.g. so that it is continuously inactive during every third or fourth duty cycle.

In the invention, it is desirable to be able to carry out a continuous and finer graduated auxiliary control, where 10 is not worked with an interruption of the lubrication function, but with an automatically controlled, continuous modulation thereof.

This is also taken into account by a previous proposal, cf. JP 1,299,007. Here, the drive shafts 15 cooperate with one end of the respective rocker arms, which immediately transmit the cam pressure to the pump piston, while the rocker arms which can rock a common shaft abut at their opposite ends against the said set screws, from which they are released under the working layer by the associated pump pistons. . Hereby the starting positions of the rocker arms and thus the pump pistons can be individually adjusted. Said common rocker shaft is arranged in eccentric bearings so that it can change the position of all the rocker arms simultaneously from outside. If these are thereby moved further towards the set screws and pump pistons respectively, this will result in a further move in of the starting position of the pistons, ie. in a general reduction of the stroke lengths, regardless of the individual positions.

While this in itself is an attractive control option, however, the device in question presents some noticeable disadvantages as a result of the eccentric movement of the rocker shaft, a movement of the rocker arms not only towards or away from said parts, but also across this direction whereby the effective arm lengths will be changed. This DK 169589 B1 3 implies that the drive knobs will hit the rocker arm transmitters sooner or later depending on the setting of the rocker shaft, thereby compromising the accuracy of the dosing times relative to the movement of the motor piston.

It is an object of the invention to provide a lubricator of the kind in which the respective collective adjustment of the individually adjustable strokes can be achieved without any associated temporal movement of the piston pump operating periods.

It will be achieved in accordance with the invention that the lubricator is arranged as defined in the characterizing part of claim 1. Hereby a collective movement of the adjusting screws is worked in and away from the rocker arms, which provides precisely the desired adjustment possibility and since the positioning of the rocker arms remains unchanged, there will be no time lag in the engagement between the drive knobs and the associated ends of the 20 rocker arms, ie. the lubrications will not be delayed by the collective regulation.

In accordance with the claims 2 and 3, the device according to the invention can be realized in a simple manner as or by a modification of an already existing lubricating unit.

Claim 4 indicates a particularly convenient device for obtaining a particular desired characteristic of the collective regulation.

As mentioned, the known regulation of the use of the eccentric bearing of the rocker arms is problematic in the graduated regulation considered here, but there may be situations where very special lubrication criteria occur in which that type of regulation is particularly applicable. It will be seen that the invention will in no way exclude the fact that the assembly is further provided with a control device of the known type DK 169589 B1 and that, cf. Claim 5 can be operated with two different control systems, quite advanced possibilities are obtained with regard to regulation according to additional criteria.

5 The invention will now be explained in more detail with reference to the drawing, in which: FIG. 1 is a perspective front view of a lubricator of the type in question; FIG. 2 is a cross-sectional view thereof; FIG. 3 is a similar view of the apparatus modified in accordance with the invention; FIG. 4 is a perspective view of certain of FIG. 3; and FIG. 5 is a plan view of a detail in a modified embodiment of the invention.

The FIG. 1, with fully drawn lines, the lubricating apparatus shown is of conventional type and is arranged next to a cylinder in, for example, a ship diesel engine, which cylinder has a number of lubrication points which continuously or impulsively must be supplied with lubricating oil from the lubricator.

This comprises an apparatus housing 2 with a drive shaft 4 connected to the main shaft of the motor for synchronous rotation therewith, and the shaft 4 can be directly connected to the corresponding shafts in a series of arranged lubricators next to a corresponding row of motor cylinders.

The lubricator has a series of built-in piston pumps driven by the shaft 4 and supplied with oil from a common stock, whereby the individual pumps send oil 30 through respective flow indicator tubes 6 and on to upper outlet nozzles 8, from which oil is passed through lines 10 to the respective lubrication points on the engine cylinder. Each of the piston pumps includes a set screw 12, which in the manner mentioned below can be adjusted to adjust 35 the stroke length and thus the capacity of the associated pump, whereby the oil supply to the different lubrication points can be graduated as needed. As mentioned, the pumps have so far been adjusted to meet the need for full load of the engine.

In FIG. 2 is a schematic representation of the detailed arrangement of the lubricating apparatus with respect to one of the said piston pumps. This pump, generally designated 14, is located in a horizontal position off the shaft 4 and a piston rod projecting from the pump. 16 has a head 18 which is innermost held outwardly from the pump by a spring 20 10 and ultimately abuts a pump shoe 22 which is held on the lower end by a vertical rocker arm 24 rotatable about a horizontal through shaft 26. The pump shoe 22 is arranged to push the piston rod 16 inwardly into the pump 14 under the influence of a cam 15 28 mounted on the shaft 4, thereby causing the rocker arm 24 to tilt accordingly around the shaft 26.

The rocker arms 24 have a projecting arm portion 30, the upper end portion 32 of which forms an abutment against the inside end of the housing 2 of the associated aforementioned set screw 20 12. This extends loosely slidably through a bore 34 in the front plate of the apparatus and is provided with a nut. 36, which rests against the inside of the faceplate.

When the pump shoe 22 is unaffected by the cam 28, the spring 20 will push the pump shoe 22 inwardly into the apparatus to a position 25 in which the upper end portion 32 of the rocker arm 24 engages the end of the set screw 12, i. the position of the adjusting screw 12 will be crucial to the resting position of the piston rod 16. If the adjusting screw 12 is screwed inwardly into the apparatus, the piston rod 16 will be pressed outwardly and, with the successive stresses of the cam 28, the pump 14 will be actuated with a correspondingly shorter stroke length. and thus a correspondingly reduced capacity.

When the cam 28 influences the pump shoe 22 for depressing the piston rod 16, the upper end portion 32 of the rocker arm 24 35 is moved away from its abutment toward the adjusting screw 12, ie. this DK 169589 B1 6 does not in any way prevent the movement in question. In so far, the set screw 12 could be in fixed screw connection with the front plate of the appliance / but this is unnecessary all the while the nut 36, which in the resting state is pressed against the inside of the front plate of the appliance, will, precisely at this pressure, be thus prevented from turning, that the desired axial adjustment of the adjusting screw can nevertheless be carried out simply by a simple turning thereof.

Hereby, the aforementioned individual adjustments 10 of the performance of the individual piston pumps can be made by individual adjustments of the set screws 12, and it is furthermore well known that an adjustment common to all the pumps can also be made in that the fixed shaft 26 for the rocker arms 24 may be eccentrically mounted in the apparatus housing 2 so that it can be moved slightly in the horizontal plane by rotating an outer end portion 38 (Fig. 1) of this shaft by a pivot handle 40.

As mentioned, it is recognized by the invention that the consumption of lubricating oil can be reduced by further limiting the performance of the 20 individual piston pumps in response to the decreasing engine load, and in connection with the lubricant described herein, this is achieved in a simple manner by providing a automatically induced change of the resting position of the piston rods 16 in response to 25 changes in engine load, so that the effective stroke length of the pumps is reduced accordingly.

Various control parameters can thus be used to express the engine load, but in a preferred embodiment of the invention the simple fact that the engine load must ultimately be given by the fuel supply to the engine is served. This supply is normally controlled by a rotatable fuel shaft, which thus expresses the engine's load state during its rotation. This rotation can be caused by a simple mechanical transmission to cause a regulatory displacement of the stops which limit the stroke length of the piston pumps, which is further illustrated in 1, 3 and 4.

It is shown in FIG. 1 is shown punctured that on top of the apparatus housing 2 may be mounted a mounted box 42, from which extends a shaft 44 ending in a radial alarm 46. This is 10 through a rod 48 connected to a radial alarm 50 on a shaft 52 which constitutes the engine's fuel shaft, which is rotated through a small angle to control the engine from idle to full load. It will be understood that the rotational movement of the fuel shaft will be transferred to shaft 44. This may optionally extend to the next lubricator in the row so that there does not have to be an arm connection 46,48,50, between shaft 52 and each of the lubricants. .

As shown in FIG. 3 and 4, the shaft 44 inside the box 42 is provided with a series of downwardly extending fork arms 54 which are arranged 20 over each of the set screws 12 and are in contact with them, namely that the fork arms of the fork arms extensively support a nut 56 between them, said nut having an inner protruding collar portion 58 which may abut on lower curved back portions 60 of the fork branches.

25 In relation to FIG. 2, the modification is hereby introduced that a top cover 3 has been removed and replaced with the box part 42, as well as the nut 36 has been removed and replaced with the nut 56. This will be its collar 58, which, when impacted on the bow parts 60, will limit the forward travel. of the upper end 32 of the rocker arm 24 when the system is in operation, but it will still be possible to adjust the set screw 12 to the desired oil dosage at full load of the engine, since the fork arms 54 assume a well-defined position when the fuel shaft 52 is turned to its full load position. When this shaft 52 is rotated away from the full load position by reducing the engine load, the shaft 44 will be rotated such that the forks are rotated slightly backwards, thereby forcibly displacing the set screws 12 rearwardly and thereby - via the associated rocker arms 24 - pushing the pump shoes 22 slightly forward to produce a reduced stroke length of the piston pumps.

It is hereby automatically achieved that the piston pumps reduce their performance at reduced engine load, and it will be understood that the reduction will occur regardless of whether the individual pumps are pre-adjusted by the preset screws 12 for different maximum benefits. By appropriate interchange throughout the mechanical transmission system, it can be achieved that, at a given rotation of the fuel shaft 52 15, an appropriate proportional change in the stroke length and performance of the individual pumps is achieved.

The modification of the apparatus so far described, cf. FIG. 2 is immediately applicable in connection with motors operating at a constant speed of the motor shaft, since otherwise the pump performance will be quite independent of fluctuating motor loads.

Different in the case of motors whose motor shaft rotates at a load dependent speed. Here, a reduction of the performance of the oil pumps 25 at reduced engine load will be achieved in advance already because the pump actuating shaft 4 and its camshafts 28 will rotate correspondingly more slowly. However, as mentioned, there is no proportionality between the load reduction and the reduction of the engine shaft speed, and it is nevertheless extremely relevant to effect a reduction-dependent additional limitation on the performance of the lubricating oil pumps using the modified device described, although of course 9 9 169589 B1 shows that a significant part of the regulation is already satisfied by the coupling between the motor shaft and the lubricator drive shaft 4.

In general, the necessary or possible reduction 5 of the stroke lengths of the pumps will be considerably less than for motors with constant speed of the motor shaft. However, for an optimization of lubricating oil consumption, it is not sufficient to work with a corresponding down-regulated linear relationship between the rotation of the fuel shaft 52 10 and the displacement of the adjusting screws 12, since the relationship in question is exponential, as is also very characteristic in that at idle of the engine may require a relatively large supply of lubricating oil.

However, according to the invention, it is quite easy to provide such a desired, non-proportional exchange of motion between the fuel shaft 52 of the engine and the control shaft 44 of the lubricant, namely using the one shown in FIG. 5, wherein the control shaft 44 is provided with a laterally extending cam follower arm 62 which cooperates with a cam washer 64 on a separate shaft or shaft 66 which, instead of the shaft 44, protrudes from the apparatus and is connected to the fuel shaft 52 on it. in FIG. 1. It will be appreciated that, by turning 25 of fuel shaft 52 and associated rotation of shaft 66, it is possible to achieve precisely the desired transfer function between this rotation and the associated displacement of the adjusting screws 12 supported by the fork arms 54 so that the desired function of consideration of the limitation of the stroke length of the pumps can be determined by the design of the curve disc 64.

It will even be possible to work with individual controls of the individual pumps, namely by using individual curve discs for the individual pumps.

10 DK 169589 B1

It has been emphasized above that the invention can be realized by a modest modification of already existing apparatus, which is of course essential in practice, but it will be understood, however, that the invention is not limited thereto. Thus, it can very well be effected in other ways that the stroke length of the individual pumps is limited by an occurring decrease in engine load, since a stroke length restriction does not, of course, need to assume precisely the arrangement shown using rocker arms 24 or the rotary fuel-shaft 52 .

In practice, it is particularly important for the invention that a considerable saving can be achieved under the conditions where up to now an automatic reduction of lubricating oil consumption has been achieved in case of decreasing engine load, namely in the case of engine installations where a decreasing engine load results in a decreasing rotational speed of the motor shaft and hence a decreasing activation frequency of the pumps in the central lubricator.

Claims (5)

1. Central lubricator for oil supply of lubrication points on a large diesel engine cylinder and of the type containing a plurality of parallel piston pumps (14) actuated by individual actuators (24) which are reciprocated by operation of drive shafts (28) on a common rotary drive shaft (4) and individually adjustable for adjusting the stroke of the individual pumps by means of respective adjusting screws (12) arranged in screw holes on a common support member, which assembly is further of the type which is provided with guides for collective graduated change of the setting of the actuators, characterized in that these controls are constituted by the common support part (44,54) of the set screws 15 (12), which is mounted in such a way that it is slidably displaceable in the direction of adjustment of the screws, and is connected to controls (46) for determining the location of the screw holes in this direction. Lubricating assembly according to claim 1, characterized in that the common supporting part is constituted by a pivot-adjustable shaft (44) with radially projecting holding parts (54) which extends generally perpendicular to the set screws and is extremely engaged with 25 nuts (56). for the screws (12). Lubricating assembly according to claim 2, wherein the piston pumps are arranged in a common apparatus housing (2) from which the adjusting screws are projecting, characterized in that the adjustable shaft (44) is arranged inside the apparatus housing and the adjustment screws extend in a longitudinally displaceable manner. through holes in the house wall. Lubricating assembly according to claim 2, characterized in that on the apparatus housing for adjusting DK 169589 B1 12 the adjustable shaft 44 is arranged a rotatable operating means (66) which carries a curve disc (64) cooperating with a protruding from the shaft (44). cam follower (62). A lubrication unit according to claim 1, characterized in that the assembly is further of the type in which the actuating means consists of rocker arms (24) tilted securely on a common shaft (26) and wherein this shaft (26) is mounted eccentrically pivotally in the 10 device housing.