JPS6045710A - Diesel engine lubrication device - Google Patents

Abstract

PURPOSE:To lubricate necessary quantity in case of necessity regardless of engine rotation by inputting and operating a signal from an operational condition detector and having a lubricating valve nozzle eject adequate quantity of lubricating oil intermittently only while said nozzle is positioned between piston rings at upper and lower ends of a crown. CONSTITUTION:Aiming at a timing when the nozzle 35 of an oiling valve 24 is positioned between the uppermost piston ring 3' and the lowermost piston ring 3'' at every interval of, for example, about ten seconds after an electric signal of axial angle for A crank is inputted, a pulse signal is inputted to a lubricator 25 so as to have one nozzle 35 eject lubricating oil as much as, for example, adequate quantity of 0.05cc and only during said timing, for example, 0.05sec. When the pulse signal is inputted from an operation command transmitter 31 through a conductor 34 to solenoid 21' of a solenoid valve 21, the solenoid 21' is excited only for that period, and changes over the position of the solenoid valve 21 to the left, then pilot oil sent from a pilot pump 38 through a working oil tank 27 is sent into a pilot board 36 only while the pulse signal continues. Thus, the necessary amount of lubrication can be certainly performed when it is necessary.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a system for supplying lubricating oil between a cylinder inert piston crown of a diesel engine, particularly a marine diesel engine.

In such a conventional diesel engine lubrication system, the driving part of the shaft lubrication lubrication pump consists of the main shaft of the engine, the drive gear,
This was based on a mechanical system connected by a chain, etc., but in the present invention, the lubrication pump is driven independently, and the desired amount of lubrication is applied intermittently to only the required amount when needed, regardless of the rotation speed of the engine main shaft. In addition to improving the lubrication pump drive system to enable accurate lubrication, the project also involves improvements to the lubrication pump and lubrication valve themselves.

Since the drive shaft of the conventional lubricating oil pump was connected to the engine crankshaft, that is, the main shaft, it had the following disadvantages. First, since the plunger speed of the oil pump is proportional to the rotational speed of the crankshaft, the speed and pressure of the lubricating oil pumped into the oil pipe are proportional to the plunger speed. Therefore, the timing at which lubricant is filled from the lubricant valve to the piston crown and the intensity of lubricating oil flowing out change with the rotational speed of the crankshaft, making it impossible to obtain a stable supply of lubricating oil. Second, since the lubrication pump and the crankshaft are mechanically connected and actuated, it is impossible to arbitrarily change the lubrication timing or the lubrication interval. Thirdly, the discharge amount from the lubrication pump is proportional to the crankshaft rotation speed, and is proportional to the horsepower (N3.N).
: r, p, m of the crankshaft) or the discharge amount proportional to the average effective pressure in the cylinder combustion chamber (proportional to N) could not be arbitrarily adjusted.

The present invention aims to eliminate the drawbacks of such conventional products, and by installing a lubricating pump independently, the lubricant is supplied with an independent discharge amount regardless of the rotational speed of the engine crankshaft. The purpose is to be able to drive a pump and supply a reliable and stable amount of oil at engine speeds ranging from low to high speeds. Furthermore, in the invention, the operation command for the lubrication pump is given by a separate operation command transmitter, and this transmitter is activated by a signal that detects the operating state of the engine. ), the aim is to issue optimal lubrication pump operation commands.

In order to achieve this objective, the present invention provides information on the crankshaft angle, piston crown position, i.e., piston link position, operating time, lubrication level between the cylinder liner and piston ring, and the cylinder liner, which indicates the operating condition of the tasel engine. An operating state detector that detects at least one of temperature, engine speed, engine output, lubricating oil consumption, and fuel injection amount and outputs it as an electrical signal, and inputs the electrical signal of the detector. When the lubrication valve nozzle, which opens inside the cylinder liner, is located between the piston links at both the upper and lower ends of the piston crown, and only during that time, an appropriate amount of IR Yuzu is spouted from the nozzle intermittently. The present invention provides a diesel engine lubricating device characterized in that it includes an actuation signal generator that generates a pulse signal that causes a lubricating machine connected to a lubricating valve to discharge lubricating oil. The lubricant lubrication system is completely independent and is not affected by the rotational speed of the engine crankshaft, so the lubrication timing, number of lubrication times, amount of lubrication, etc. can be set as desired.

That is, an appropriate amount of oil can be applied between the piston rings every other revolution or every few revolutions of the crankshaft. Then, the engine's operating state detector detects the operating state, converts this into an electrical signal, and processes it with the operating signal transmitter.
Since the lubrication machine is actuated by this processed signal, it is possible to lubricate the oil in accordance with the operating condition of the engine. Furthermore, the lubricating machine is a mechanism that operates according to the operation command signal from the drive device, and can also have a discharge amount variable mechanism, so it can perform a pumping action according to the operation command, and the lubricating oil discharge amount can also be adjusted. It is possible to adjust steplessly from 0 to the widest discharge amount range 1 that the lubricating machine has, and it is possible to supply the required amount of lubricating oil when necessary.

Therefore, unnecessary supply of lubricating oil can be omitted, which is extremely economical.

Embodiments of the present invention will be described below with reference to the drawings.

Conventional lubricant oil filling devices are as shown in FIGS. 1, 2, and 3, for example. The piston crown (2) is connected to a crankshaft (main shaft) (8) and is installed in the cylinder liner (1) so as to be able to reciprocate. As shown in Figure 3, the drive shaft (7) of multiple lubricated θ three-oil pumps (6)
is connected to the crankshaft (8) via a chain marked a, and as the crankshaft rotates, the oil pump drive shaft rotates and the oil pump is operated. (L is the combustion chamber, and cA is the fuel valve. Figure 2 shows an example of the lubrication pump mechanism shown in Figure 1, but an eccentric cam 0 is fixedly installed on the drive shaft (7). The rotating plunger is always pressed toward the eccentric cam via the plunger lever by a return spring (14), and the plunger moves back and forth as the eccentric L cam rotates.

Plunger lever α2 is an eccentric cam (interlocked with stopper Qo) with a pin (1η as a fulcrum) that controls the stroke when plunger Q3 moves to the left in the figure, and plunger lever μ2 is It controls the flow of the plunger A.When the plunger mouth moves to the left in the figure, it is the suction process, and when it moves in the fixed direction, it is the discharge process, and the lubricating oil flows through the suction check valve and the discharge check valve. It is sent under pressure to the lubrication pipe (5) through the grout Q.There,
The lubricating oil in the lubricating pipe pushes open the lubricating valve (4) and sequentially flows into the cylinder liner (1), acting as a lubricating oil on the sliding surface 41'j when the piston crown (2) reciprocates.

The ideal action of lubricating oil is piston crown (2)
It is most desirable that the piston ring (3) flow out between the uppermost ring (3) and the lowermost ring (3), and above the uppermost ring (3)!
or the lowest end ring (if the lubricant leaks below the three rings, this amount will be completely wasted lubricant. In other words, the drive shaft (7) of the lubricant pump (6) and the eccentric cam α should be connected to the drive chain α. 3 rotates in direct proportion to the number of revolutions of the crankshaft (8), and in conjunction with this, 3 reciprocates to the plunger and performs a pumping action. I couldn't avoid it.

Next, an exemplary embodiment of the present invention will be described.
The figure is a schematic block diagram showing the entire device, and the diesel engine lubrication device includes an operating state detector (G), an operation signal generator 0υ, a lubrication machine (C), and a lubrication valve (Tai).
Furthermore, it includes a lubricating nozzle (5) and a conductor oa (3"+ <3→) that connect the above-mentioned members. The diesel engine in which the lubricating device is used is shown in FIG. This device is the same except that it does not have a built-in reed.As shown in Fig. 3, this device has eight units per cylinder of a marine diesel engine, for example. , usually multiple, oil supply valve (
C) are installed in a radial position, and their nozzles 09 open inside the cylinder liner (1).

As will be explained in detail below, in the present invention, the nozzle Q is located approximately between the uppermost ring (31) and the lowermost ring (31) of the piston ring (3) supported by the piston crown (2). An appropriate amount of lubricating oil is spouted intermittently from nozzle 0→ only at times and only during those times.

The lubrication machine (c) of the diesel engine lubrication system is installed separately from the tasel engine and is not built-in as shown in Figure 2.

In a non-embodiment, the operating state detector (G) extracts the crankshaft angle (A) as an electrical signal by a known detection device (not shown) that comes into contact with the crankshaft (8) and sends it to an operating signal generator via a conductor q2. Enter 0 sword. however,
(A) In addition to or in lieu of the crankshaft angle electrical signal, using known equipment, (B) operating time, (C
) Piston crown position, i.e. piston ring position, CD
) The degree of lubrication between the cylinder liner and piston ring, (
K) Cylinder liner temperature, (F) Engine speed,
(G) Engine output, (H) Lubricating oil consumption, (1)
Actuation signal generator 0 that takes out the fuel injection amount as an electrical signal
It may also be input to η.

The operation signal transmitter Gυ has a built-in signal processing logic, and when the detector (to) detects the operating state of the engine as an electrical signal, it is input, and this signal is processed according to predetermined signal processing logic. Then, an operation command signal is sent to the lubrication machine (c).

That is, the operation signal transmitter 0υ is the operating state signal (A).

When a signal in B, C, etc.) is detected, the signal processing logic determines what command to send to the lubricating machine. In the case of the embodiment, (A) the crankshaft angle electrical signal is input, and, for example, the oil filler valve (C)'s nozzle 09 is moved to the uppermost piston ring every 10 seconds, that is, not every engine revolution. 3 and the lowest piston ring (
The lubricating machine sends a pulse signal to eject an appropriate amount of lubricating oil, e.g. 0.05 CC, from one nozzle (3') for a period of time, e.g. 005 seconds. Enter (c).

Note: In the II1 machine (c), the pulse signal from the operation command transmitter Q via the conductor 0Φ is sent to the solenoid valve →'s lunoid (21
When this input is made, the Lunoid G2) is energized only during that time, the position of the solenoid valve Qυ is switched to the left position as seen in Fig. 4, and the pilot pump 08 is activated via the hydraulic oil tank (c).
The pilot oil sent from the pump t2 is sent to the pilot boat OQ of the pump t2 only while there is a pulse signal. (40) is an electric motor that rotates the pilot pump pqt, and (40) is an IJ-F valve, which is set to 40 to 60 f/A in the embodiment. 0υ is a pressure gauge, and 饅 is a check valve. When the pulse signal is no longer sent, the solenoid valve (2!
1'), the spool (C) is returned by the spring (G) of the oil pump (C) as explained later, and the pilot oil in the pressure chamber Q71 flows through the pilot boat OQ and the check valve 0■. and is returned to the tank (a).

Therefore, the lubrication pump (c) that operates with this pressure oil will operate with the pressure oil given an arbitrary switching pulse, and as a result, the lubricant pump (c) discharged from the lubrication pump (c) will The charge) is pumped to the lubricating pipe (5) as lubricating oil to which pulses are applied based on the command.

Figure 5 shows a lubricating pump (c) used in the lubricating device of the present invention.
A cross-sectional view is shown. In the housing (40), the spool (c) is connected to the spool upper part (4s') and the stepped part (45) and is inserted as one unit so that it can reciprocate in the vertical direction.・When the pilot oil sent from the pilot pump decoy is supplied into the pressure chamber o71 from the port □ (3Q) of the lubrication pump (c), the spool (g) (45') moves upward. When the solenoid valve (c) is turned off, that is, when no pulse signal is sent, the spool &!5 (45') is pushed back downward by the spring tt34, and the pressure chamber (inside the Pressure oil is returned to the tank (c) from the solenoid valve Q]). Lubricating oil is returned to the tank (c) from the lubricating oil tank @ by a charge pump (c) rotated by an electric motor (39) and a charge set by a check valve (g). The lubricating oil is charged into the oil chamber (52) from the supply hole (51) through the oil passage tscJ under pressure. When using low viscosity lubricating oil, use a charge pump (a) like the one in this example. Install the lubrication pump into the tank Q9) without
It can also be used as a self-inhalation type by soaking it in oil. When the spool rises, the lubricating oil charged in the oil chamber (52) by the charge pressure passes through the slanted notch (54) provided at the upper part of the spool (4s') (the edge (53) in Fig. 6). ) closes the supply hole (5) and increases the pressure in the oil chamber (52), and the spring (56) is pushed up by the poppet (5), and the spool (5) fills the lubricating oil in the oil chamber (52). Once every rising start and therefore once every time the solenoid valve Q]) is switched, /
Supply to 4E oil tank (c).

The upper part of the spool (45 is the lever (57) and the flat surface (58)
) is connected at the part that connects the spool (45), and the spool (45) is allowed to move up and down, but when the lever (57) is rotated, it is rotated in the circumferential direction around the axis of the spool 0Q. (Fig. 7). Correspondingly, the axial position at which the edge (53) of the inclined notch (54) closes the supply hole (51) is cl, d''a+ in Fig. 6. At the position of the solid line shown at 57°C, the circumferential groove (55) communicates with the supply hole (5) when the spool (9) is pushed up to the uppermost position, so the amount of lubricant discharged is 0, and the maximum discharge amount is reached at the position of the lever (57').α indicates the operating range.The lever (57) is manually operated, for example, after the engine has been driven for a certain break-in period, the maximum amount of force is set to the position. (57) may be changed to the intermediate oil amount.As shown in Fig. 4, the operating signal generator 0]
) or a timer activation signal may be input to the servo device (SV) via the conductor 03, and the lever (57) may be rotated via a ring mechanism (not shown) to vary the lubricating oil discharge amount of the oil pump 12t9.

In FIG. 5, the force/force/servo device (sv), etc. are not shown.

In this example, pilot pump No. 6 and solenoid valve Q]
) and oil pump? It will be clear to those skilled in the art that although the Q and Q are separate bodies, it is also possible to make them both '4i bodies and have the spool 0→ directly driven by a solenoid.

As mentioned above, the lubricating machine (c) has a variable discharge rate mechanism, which allows the amount of lubricant to be supplied to the cylinder liner to be adjusted arbitrarily, eliminating unnecessary supplies and providing an economical lubricant supply. It becomes possible. In order for the lubricating device of the present invention to function better, the lubricating valve (c) that injects lubricating oil also plays an important role.

The function of the lubrication valve (c) will be described below based on Fig. 8.

The lubricating oil discharged from the lubricating pump Q of the lubricating machine (c) is sent to the lubricating valve (c) via the lubricating pipe (5).

The lubricating oil sent to the oil supply valve passes from the port (59) through the passage (62 bars 63 x 64 bars 65 x 66) to the pressure chamber (69).
). The pressure oil led to the pressure chamber (69) is passed through the poppet (
6x) is ejected from the nozzle by pushing it downward in the figure.

The poppet (61) is pushed downward in the figure via holder A (70) and holder B (71) by a setting force of a spring (6), and is received by a square W C72). The passageway (66) opens into a hole provided in the poppet surface (67) and communicates with the pressure chamber (69). The setting force of the reed spring (60) is given by lowering the adjustment screw (75) which is inserted into the main body (74). The pressure oil that has flowed into the pressure chamber (69) is connected to the poppet surface (67).
) When the force generated by acting on the spring (6) overcomes the setting force of the spring (6), the poppet (61) moves upward and lubricating oil is spouted from the nozzle 06. (spring setting pressure), and the lubricating oil is injected to the piston crown when the valve is opened due to the pressure released.The preferred opening pressure is about 20 f/d to 100 f/d, about 1 High pressure is preferred.

The injection state at this time is, for example, if the valve opening pressure is set to 40'yfμ, the internal pressure of the oil supply pipe (5) is 40"y,
The valve is opened when f'/c1 or more. Since the fuel is injected at high pressure at the same time as the valve opens, it is injected extremely vigorously. Further, the oil supply valve is closed instantly when the internal pressure of the oil supply pipe becomes 40'if/lyi or less in the above case, so that only the effective amount is injected, which is extremely economical.

The pressure drop in the internal pressure of the lubricating pipe occurs as soon as the spool (G) reaches the top dead center (discharge process end point) as shown in FIG. ) can be obtained by communicating with

From the above, the lubrication machine has a function that can fully respond to the operation command from the operation command transmitter, and the reed and lubrication valve also have a function that can reliably and forcefully inject the lubricating oil that is pumped from the lubrication machine. There is. Therefore, in order to inject the piston ring (between the uppermost ring and the lowermost ring) installed in the piston crown, which is the final goal, a signal from the operating signal transmitter that detects the operating state of the engine is given to the lubrication machine. As a result, the lubrication function of this device is satisfied.

In the configuration of this embodiment, since the lubrication device is installed independently, the lubrication timing, the number of lubrication times, and the amount of PE oil can be arbitrarily set regardless of the rotation of the engine crankshaft. The setting is such that the operating condition detector detects the engine operating condition, and the operating signal transmitter processes the electrical signal and sends it to the lubrication machine as an optimal operation command signal pulse to operate it, so the operating condition of the engine is determined. It is possible to lubricate according to the conditions.

Furthermore, since the lubrication pump of the lubrication machine is a variable discharge type,
For example, after a certain period of time has elapsed, lubricating oil can be further saved by changing the discharge amount manually or using a signal from a slow timer. The lubricant valve is a differential pressure differential mechanism that closes instantly immediately after injection is completed, and the residual pressure in the lubricant pipe prevents the oil from dripping even after injection.Furthermore, the lubricant valve has a single outlet. Since the nozzle hole is of a certain size, it is not affected by the pressure inside the cylinder combustion chamber, so it can fully perform its injection function into the cylinder.

Since the device of this embodiment is not built into the diesel engine, it can be manufactured at a price of about 1/2 or less compared to conventional products, and since lubricating FV1 oil is not constantly dripped, the lubricating oil is less than about 172 mm compared to conventional products. We were able to obtain extremely good results, such as being able to save a lot of money.

[Brief explanation of drawings]

Fig. 1 is a schematic layout of a conventional product, Fig. 2 is a schematic structure of the lubricating pump shown in Fig. 1, and a plan view including a sectional view of section f1. Fig. 3 is a hydraulic circuit diagram of the lubricating device shown in Fig. 1. 4 is a schematic block diagram of an exemplary embodiment of the present invention, FIG. 5 is a sectional structural diagram of the oil pump, FIG. 6 is an enlarged perspective view of part B in FIG. 5, and FIG. 7 is a schematic block diagram of an exemplary embodiment of the present invention. is a cross-sectional view taken along line A-A in Fig. 5, and Fig. 8 is a cross-sectional structural diagram of the lubrication valve shown in Fig. 4. 1... Cylinder liner 2... Piston crown 3... ... Piston ring 5 ・ Pipe 8 ... Crankshaft 21 ... Electromagnetic square 24 ... Note ? Mountain ㅅf25 ...
・Note Oil (Iku 26...Oil pump 30...Operating status detector 31...Operating signal transmitter 35...) Zuru 38...Pilot pump 45... Spool 46... Housing 51... Supply hole 54... Notch 57... Lever device (variable mechanism) 60...・・・
... Spring 61 ... Poppet 67 ... Poppet surface 58 ... Tip, 9 ... Pressure Office Attorney Patent Attorney Jun Kawachi Figure 5 Figure 8 Q-

Claims (6)

[Claims] (1) Crankshaft angle, piston crown position, i.e. piston ring position, which indicates the operating condition of the diesel engine;
Detects at least one of the following: operating time, degree of lubrication between the cylinder liner and piston ring, cylinder liner temperature, engine speed, engine output, lubricating oil consumption, and fuel injection amount, and outputs it as an electrical signal. An operating state detector inputs the electrical signal of the detector and performs arithmetic operations. When the oil fill valve nozzle that opens into the cylinder liner 1111 is located approximately between the piston rings at both the upper and lower ends of the piston crown, only during the force and hemorrhage period. and an actuation signal generator that generates a pulse signal that causes a lubricating machine connected to a lubricating valve to eject lubricating oil so that the entire appropriate amount of lubricating oil is intermittently spouted from the nozzle. Device. (2) The lubricating machine has a manual variable mechanism for varying the discharge amount for each pulse signal, or an automatic variable oil PA mechanism based on the activation signal of the signal generator reed or timer. Diesel engine lubrication device as described. (3) The lubricating machine includes a solenoid valve that supplies pilot oil from the pilot pump to the pilot chamber of the lubricating pump once for each pulse signal, and an appropriate amount of lubricating oil to the lubricating valve each time the pilot oil is sent. A diesel engine lubrication device according to claim 2, further comprising: a lubrication pump for supplying oil; (4) The lubricating valve is configured to spout only when the pressure of the lubricating oil sent from the lubricating machine is at a high pressure of approximately 20 KyfAa to 100 f/-1. The diesel engine lubricating device according to item 3 which spans item 2. (5) The diesel engine according to claim 1, wherein the operating state detector detects the crankshaft angle as an electric signal. IIH device. (6) The lubrication pump includes a spool that reciprocates once for each use of the pilot oil in the housing hole, and a lever connected to allow the spool to reciprocate and rotate the spool in the circumferential direction around the spool axis. Claim 3, comprising: a device; and a spool upper portion provided with beveled notches at different axial positions to close a lubricating oil supply hole opening in a rotation housing hole of the lever device. Diesel engine lubrication device as described in Section 1. a poppet biased by a spring having an adjustable biasing force, and a pressure chamber formed by the poppet surface other than the tip end where the lubricating oil path opens and the inside of the main body hole. A diesel engine lubricating device according to claim 3 or 6.