JP2010025068A - Cylinder lubricating device of pressure-wave oil delivery type - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cylinder lubricating device by which while taking advantages of a low-cost mechanical type, oil-delivery can be sufficiently effected even under increasing pressure associated with the passage of a piston in a cylinder. <P>SOLUTION: In the cylinder lubricating device, lubricating oil U is conducted to a lubricating nozzle 2 installed in a cylinder-sidewall 1 of a diesel engine so as to be injected in a cylinder chamber 3. The cylinder lubricating device includes an oil delivery device 11 which delivers a predetermined amount of lubricating oil in synchronization with rotation of the engine; an oil-delivery pipe 12 which delivers the lubricating oil delivered from the oil delivery device 11 to the lubricating nozzle; an oil-pressurizer 13 which is provided with a check-valve function, and pressurizes the oil delivered from the oil delivery device to generate pressure waves, and delivers it to the oil-delivery pipe; and an oil straightener 14, which is installed on this side of the lubricating nozzle, having the check-valve function, and a straightening hole of a trapping space for trapping pressure reflection-waves of the oil conducted through the oil-delivery pipe, thus to straighten the pulsation of the pressure waves. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a lubricating oil supply device in, for example, a diesel engine.

  Generally, in a large diesel engine for marine use, lubricating oil (also referred to as cylinder oil) is supplied to a piston ring part of a piston from an oil filling port formed in a cylinder side wall part of the engine. There is a formula.

  As shown in FIG. 11, this mechanical lubrication device is provided in the plunger chamber 53 so as to be freely retractable in the middle of the lubrication oil supply path 51 that leads the lubrication oil from the lubrication oil tank to the lubrication nozzle provided on the cylinder side wall. A plunger-type pump 52 having a plunger 54 is provided, and the plunger 54 is driven by a cam 56 rotated in conjunction with an engine via a rocker arm 55, and the lubricating oil supply The passage 51 is provided with a pair of check valves 57 and 58, and the pump 52 is connected to the lubricating oil supply passage 51 between the check valves 57 and 58 (for example, Patent Document 1 and Non-Patent Document 1). Patent Document 1). An adjustment screw 59 for adjusting the stroke is provided at one end of the rocker arm 55.

By the way, in order to operate the plunger 54, there is an electrohydraulic type instead of the mechanical type using the cam as described above.
In this electrohydraulic type, the plunger is retracted and retracted at high speed by supplying and discharging the hydraulic pressure to and from the cylinder chamber instead of retracting the plunger by a cam (for example, Non-Patent Document 1). reference). Therefore, this electrohydraulic type can supply lubricating oil with high pressure.
JP 59-185812 A Journal of the Japan Marine Engineering Society Vol.37 No.2 (2002-2); New cylinder lubrication method

  In the lubrication device, it is preferable to lubricate the lubricating oil at the timing when the piston ring of the engine is passing or before passing, but in the case of a mechanical type, the lubricating oil ejected from the lubricating nozzle provided on the cylinder side wall of the engine The amount decreased due to an increase in pressure in the cylinder accompanying the passage of the piston, and there was a problem that lubrication at a predetermined position could not be sufficiently performed.

  On the other hand, in the case of the electrohydraulic type, even if the pressure in the cylinder increases as the piston passes, it can be lubricated without reducing the amount of lubricating oil, but on the other hand, new hydraulic generators, electronic control circuits, etc. There was a problem that the addition of equipment and measures against electrical troubles were necessary, and the cost of the lubrication equipment was high.

  Furthermore, in the case of an electrohydraulic type, the amount of lubricating oil injected per time is larger than that of a mechanical type, so it is necessary to control (limit) the amount of lubricating oil in terms of time, for example, thinning out the number of times of lubricating oil, etc. Therefore, there is a problem that a cycle in which no lubrication is performed occurs and a lubricating oil film cannot be sufficiently formed on the inner wall surface of the cylinder.

  Therefore, the present invention can sufficiently lubricate even when the pressure in the cylinder increases due to the passage of the piston while taking advantage of the low cost mechanical type, and lubrication of the lubricating oil per time A pressure wave oil feeding type cylinder oiling device capable of oiling without reducing the amount and thinning out the number of times of oiling is provided.

In order to solve the above problems, a pressure wave oil supply type cylinder oil supply device according to claim 1 of the present invention introduces lubricating oil into an oil supply nozzle provided on a cylinder side wall portion of a diesel engine and injects the oil into a cylinder chamber. Because
An oil delivery section for delivering a predetermined amount of lubricating oil in synchronization with the rotation of the engine, a lubrication oil supply passage for supplying the lubrication oil sent from the oil delivery section to the lubrication nozzle, and a check valve function; An oil pressurizing unit that pressurizes the lubricating oil delivered from the oil delivery unit to generate a pressure wave and delivers the pressure wave to the lubricating oil supply path, and is disposed in front of the oiling nozzle and has a check valve function and the lubrication And an oil rectifier that rectifies pressure wave pulsation by having a confining space that can confine a pressure reflected wave of the lubricating oil guided through the oil supply path.

Further, a pressure wave oil supply type cylinder oil supply device according to a second aspect of the invention is characterized in that the oil pressurizing unit in the oil supply device according to the first aspect has a large-diameter first oil passage for guiding lubricating oil from the oil delivery unit and A pressurizing portion main body formed with a second oil passage having a small diameter communicating with the first oil passage, a first valve body disposed on the second oil passage side and capable of opening and closing the opening of the first oil passage; A first biasing member capable of biasing the first valve body toward the first oil passage and closing the opening;
A rectifying unit body in which a small-diameter third oil passage for guiding lubricating oil from a lubricating oil supply passage and a large-diameter fourth oil passage communicating with the third oil passage are formed, and the fourth oil A second valve body disposed on the passage side and capable of opening and closing the opening of the third oil passage, and a second urging force that urges the second valve body toward the third oil passage and closes the opening. It is comprised from the member.

  Further, the pressure wave oil supply type cylinder oil supply device according to claim 3 is the size of the first valve body in the oil supply device according to claim 2, and the projected area of the first valve body with respect to the oil passage cross section is: The opening area of the first valve body is approximately five times larger than the opening area.

  According to a fourth aspect of the present invention, there is provided a pressure wave oil feeding type cylinder lubricating device, wherein the first valve body in the lubricating device according to the second or third aspect is made of a magnetic material, and the first valve body is first biased. An electromagnet that can be urged in the same direction as the urging direction of the member is provided in the pressurizing unit body.

  Further, in the pressure wave oil supply type cylinder oil supply device according to claim 5, the inner diameter of the oil supply hole provided in the oil supply nozzle in the oil supply device according to any one of claims 2 to 4 is gradually decreased toward the tip. It is a thing.

  Furthermore, the pressure wave oil supply type cylinder oil supply device according to claim 6 is configured such that an injection port formed at the tip of the oil supply nozzle in the oil supply device according to any one of claims 2 to 5 has an injection direction of the cylinder chamber. The inner wall surface is formed in a direction along the circumferential direction.

  According to the configuration of the pressure wave oil feeding type cylinder lubrication device, when sending the lubricating oil to the lubricating oil supply passage between the oil sending section and the lubricating oil supply passage, the pressure wave is transmitted with a check valve function. Since the oil pressurizing section that can be generated is provided, the lubricating oil can be supplied to the oiling nozzle at a high pressure, and therefore, the lubricating oil can be reliably jetted into the cylinder at a predetermined timing, that is, the oiling can be performed.

  Further, the oil pressurizing part has a check valve function, that is, it is a mechanical type instead of an electrohydraulic type, so it has a simple and inexpensive configuration and is equivalent to an electrohydraulic type. Function can be demonstrated.

  In addition, since the oil rectifier that rectifies the pulsation of the pressure wave is provided with a confining space that can confine the pressure reflected wave of the lubricating oil guided through the lubricating oil supply path, a reverse flow flows from the lubricating nozzle side. Pressure wave, i.e., reflected pressure wave, can be prevented from being transmitted to the lubricating oil supply path side, and thus the pressure between the oil pressurizing unit and the oil rectifying unit can be stabilized. The pressure wave can be reliably guided to the lubrication nozzle side.

  In addition, by providing an electromagnet that can attract the first valve body, when opening and closing responsiveness of the valve body is required, such as during high-speed rotation, combining the biasing force of the spring body and the electromagnetic force of the electromagnet It becomes possible to control the lubrication timing with high accuracy.

  Furthermore, the pressure of the lubricating oil can be further increased by gradually narrowing the lubricating oil supply path downstream from the oil rectifying unit.

Hereinafter, a pressure wave oil feeding type oiling device according to an embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, this pressure wave oil supply type oil supply device guides lubricating oil U to an oil supply nozzle 2 provided on a cylinder side wall 1 of a diesel engine, and a small jet port (described later) provided at the tip thereof. ) To be injected into the cylinder chamber 3.

  That is, the pressure wave oil supply type oil supply device is roughly divided into an oil delivery device (oil delivery unit) 11 for delivering a predetermined amount of lubricating oil in synchronization with the rotation of the engine, and the oil delivery device 11 for delivery. Lubricating oil supply pipe (lubricating oil supply passage) 12 for supplying the lubricating oil to the oil supply nozzle 2 and the lubricating oil sent out by the oil feeder 11 are pressurized to a predetermined pressure to generate a pressure wave and lubricate. An oil pressurizer (oil pressurization unit) 13 sent to the oil supply pipe 12 and a pressure wave of the lubricating oil generated by the oil pressurizer 13 reach the oil supply nozzle 2 and a hole for oil supply (described later). And an oil rectifier (oil rectifier) 14 capable of preventing the reflected pressure wave reflected by the inner wall surface from being transmitted to the oil pressurizer 13 side.

  As shown in FIG. 2, the oil delivery device 11 is provided on a side wall portion 21a of a storage tank 21 for storing lubricating oil U, and one end portion is provided through a hole portion 21b formed in the side wall portion 21a. A block body 22 formed with a lubricating oil passage, that is, an oil delivery hole 22a that is communicated with the other end and opened to the outside, and a pair of oil is provided in the middle of the oil delivery hole 22a of the block body 22. The suction-side check valve 23 (23A, 23B) and the discharge-side check valve 24 (24A, 24B), which are provided respectively, are connected to and connected to an oil delivery hole 22a between the check valves 23, 24. And an oil supply unit 25.

  The oil supply unit 25 has a plunger chamber (also a hole) 26a at the center and a cylindrical member 26 connected so that the distal end side is inserted into the side wall 21a, and a plunger chamber 26a of the cylindrical member 26. Provided between the inserted plunger (which is also a piston member) 27 and a head portion 27a of the plunger 27 and the outer periphery of the cylindrical member 26, the plunger 27 is biased in a direction protruding from the plunger chamber 26a. And a coil spring 28 for the plunger.

  In the storage tank 21, a rocker arm (arm member) 32 is swingable about the support shaft 31 via a support shaft 31, and one end thereof can come into contact with the head 27 a of the plunger 27. And a cam 33 that is linked to the crankshaft of the engine and pushes the head portion 27a of the plunger 27 against the urging force of the plunger coil spring 28. A screw member 34 is provided on the storage tank 21 side at a position corresponding to the other end side of the rocker arm 32 to adjust the rocking amount of the rocker arm 32, that is, the amount of lubrication.

  As shown in FIG. 2, the oil pressurizer 13 is formed with a large-diameter first oil hole (first oil passage) 41 a having one end communicating with the oil discharge hole 22 a of the oil transmitter 11. And a pressurizer having a small-diameter second oil hole portion (second oil passage) 41c communicated with the first oil hole portion 41a via a narrow-diameter communication hole portion 41b on the other end side. A main body (an example of a pressurizing section main body) 41, a spherical first valve body 42 that is disposed in the second oil hole 41c and that can open and close the communication hole 41b, and the first valve body 42 And a first coil spring (an example of a first urging member) 44 that urges the first valve body 42 in a direction to close the communication hole 41b via a holding member 43. That is, the check valve function is exhibited by the first valve body 42 and the first coil spring 44, and in this sense, it can also be called a check valve.

  As shown in FIG. 3, the cross-sectional area S1 of the communication hole portion 41b is approximately 1/5 of the projected area S2 of the first valve body 42 (S1 / S2 = 1/5 or a value close to 1/5). Has been. That is, the seating area of the first valve body 42 is greatly increased and the mass thereof is also increased. In other words, it means that the valve does not open at a slight pressure. Incidentally, a normal check valve has a seating area as small as possible and a small mass, so that the valve opens with a little pressure.

  As described above, unlike the normal check valve, the first valve body 42 having the check valve function according to the present embodiment dares to set the seating area as the pressure receiving area (the opening area of the communication hole 41b). The valve is not opened with a little pressure by making it much larger than (some) and increasing its mass.

  Therefore, the lubricating oil delivered from the oil delivery device 11 is similar to a normal check valve in that the pressure acting on the inlet side pressure, that is, the pressure acting on the pressure receiving area exceeds the urging force of the first coil spring 44 (this pressure is increased). Until it reaches the open pressure), it is mainly dammed in the first oil hole 41a and is in a pressure accumulating state (in this sense, the first oil hole 41a is connected to the pressure accumulating portion or the pressure accumulating chamber). If the oil pressure exceeds the opening pressure and the lubricating oil flows into the second oil hole 41c, the oil pressure acts not only on the pressure receiving area but also on the seating area, and the opening pressure rapidly increases. Decrease (so-called avalanche phenomenon). At this time, the amount of injected lubricant (the amount of lubrication) that has been accumulated is accelerated at a stretch until the opened first valve body 42 is closed again, and is sent out at a high speed. Also descends instantly. This action is the same as operating the plunger at a high speed. In other words, it is the same as operating the plunger by hydraulic pressure in the electronic lubrication system, that is, the electrohydraulic system. Thus, since the first valve body 42 is opened at a high speed with the pressure of the lubricating oil increased, a pressure wave can be generated and the lubricating oil can be brought into the lubricating oil supply pipe 12 by the pressure wave. Can be sent out.

Next, the oiling nozzle 2 and the oil rectifier 14 will be described.
As shown in FIGS. 1 and 4, the oil rectifier 14 and the oiling nozzle 2 are integrally combined and attached to the cylinder side wall 1.

  The nozzle body 2a of the oiling nozzle 2 is formed in a cylindrical shape, and a small-diameter hole (an example of an oiling hole) 2b is formed on the distal end side of the nozzle body 2a and on the proximal end side. Is formed with a large-diameter hole (an example of a hole for oiling) 2c, and on both sides of the tip of the nozzle body 2a, a very small-diameter jet port 2d capable of jetting lubricating oil is formed. Yes. As shown in FIG. 5, the direction of the jet outlet 2d is not toward the center of the cylinder chamber 3 but toward the inner wall surfaces on both sides [To be exact, the inclined groove portion (tip is formed on the cylinder side wall portion 1). The groove portion (which becomes shallower) 1a] is circumferentially arranged so that it can be ejected.

  Further, as shown in FIG. 4, the oil rectifier 14 has a small diameter oil introduction hole 51a formed on one end side which is the lubricating oil supply pipe 12 side and a large diameter on the other end side which is the oil supply nozzle 2 side. A rectifier body (an example of a rectifier main body) 51 in which a rectifying hole (an example of a confining space) 51b is formed, and a spherical second valve body 52 disposed in the rectifying hole 51b, The second valve body 52 includes a second coil spring (an example of a second urging member) 53 that urges the second valve body 52 toward the oil introduction hole 51a. Therefore, the second valve body 52 and the second coil spring 53 can exhibit a check valve function, similarly to the first valve body 42 and the first coil spring 44 in the oil pressurizer 13.

  In this oil rectifier 14, the pressure wave generated by the oil pressurizer 13 passes through the oil introduction hole 51 a and the second valve body 52, reaches the oil supply nozzle 2 side, and enters the cylinder chamber 3 from the outlet 2 d. Erupted.

  By the way, a part of the lubricating oil is reflected by the inner wall surface of the large-diameter hole 2c of the lubricating nozzle 2 and returns to the oil rectifier 14 side again. Return to the supply pipe 2 side is prevented. That is, the oil having the inertial energy that is reached as “dense” of the pressure wave is instantaneously put into the space near the lubrication nozzle 2, that is, in the straightening hole 51b and the large-diameter hole 2c, particularly in the straightening hole 51b. Can be trapped inside. In other words, the lubricating oil delivered at a high speed as a pressure wave can be ejected from the lubricating nozzle 2 at a high speed using inertia force without killing the initial speed. The rectifying hole 51b can be referred to as a confining space in which lubricating oil can be confined, and in a broad sense, the rectifying hole 51b and the holes 2b and 2c on the lubrication nozzle 2 side. Can also be referred to as a confining space.

  In the above configuration, when the engine is rotated, the cam 33 is rotated, and the plunger 27 is moved out and with a predetermined stroke via the rocker arm 32. Of course, the return operation of the plunger 27 is performed by the biasing force of the coil spring 28.

  In this way, when the plunger 27 is withdrawn and withdrawn with a predetermined stroke, the lubricating oil U corresponding to the volume is sucked from the suction side check valve 23 and then to the oil pressurizer 13 via the discharge side check valve 24. Sent out.

  When the lubricating oil U is sent out to the oil pressurizer 13, the pressure acting on the pressure receiving area on the inlet side is blocked by the first oil hole 41 a and accumulated until the force acting on the coil spring 28 is exceeded. However, when the oil pressure exceeds the opening pressure and the lubricating oil U flows out, the opening pressure rapidly decreases due to the oil pressure acting not only on the pressure receiving area but also on the seating area. At this time, the accumulated oil is accelerated at a stroke until the first valve body 42 once opened is closed again and flows out at a high speed, so that the accumulated oil pressure also drops instantaneously. This effect is the same as the effect of operating the plunger at a high speed, in other words, the same as the operation of the plunger at a high speed using hydraulic pressure, that is, using an electromagnetic switching valve, as in an electronic lubrication system. . Therefore, the lubricating oil can be supplied (guided) to the oiling nozzle 2 at a high speed as in the electrohydraulic type, though it is a mechanical type. In this sense, the oil pressurizer 13 can be called a pulse converter.

  FIG. 6 shows a waveform diagram of the lubricating oil pressure A generated by the oil pressurizer 13 and the lubricating oil pressure B reaching the lubricating nozzle 2. As shown in FIG. 6, by providing the oil pressurizer 13, the oil sent out from the plunger 27 is temporarily stopped, and the lubricating oil pressure on the oil pressurizer 13 side reaches a peak like a waveform A in proportion to the lift characteristics of the cam 33. It can be seen that the pressure has risen up to the opening pressure.

  When the pressure of the lubricating oil exceeds the urging force of the coil spring 28, that is, the set pressure, the communication hole portion 41 b is opened, and a high-pressure pressure wave advances toward the lubricating nozzle 2 through the lubricating oil supply pipe 12. Since the pipe flow velocity at this time is increased by the oil pressurizer 13, it is faster than the pipe flow velocity in a normal mechanical type. That is, the pressure wave reaching the oil injection nozzle 2 contributes to the direction of increasing the oil ejection speed, so that the pressure is efficiently converted into the speed.

  As described above, a very high-speed pressure wave is generated in the oil pressurizer 13 and instantly propagates to the oil supply nozzle 2, so that it is possible to eliminate variations in the oil supply amount and the oil supply timing that have been problematic in the mechanical system. In addition, since the propagation speed of the pressure wave is very high, adverse effects such as the case where the length of the lubricating oil supply pipe 12 varies depending on the lubrication location of the cylinder are reduced.

  FIG. 7 shows waveform diagrams of an oiling pressure C, a mechanical oiling pressure D, and an electrohydraulic oiling machine side pressure E in the present embodiment. FIG. 7 clearly shows that a higher pressure wave is generated when the oil pressurizer 13 is provided. In the conventional mechanical type, the pressure is as low as about 0.5 MPa, and in the electrohydraulic type, the pressure is about 2 MPa, whereas in the present embodiment, the pressure can be increased from 3 to 7 MPa. is there.

  In addition, as described above, the oil rectifier 14 and the oiling nozzle 2 are disposed apart from each other, and an appropriate volume portion (a space portion) is provided between the two, thereby generating pressure generated in the oil pressurizer 13. Waves can be instantly confined in this volume.

  That is, when there is no volume portion, as shown in FIG. 8B, when a reflected wave is generated, high-frequency noise (indicated by a two-dot chain line F) is generated in the vicinity of the lubrication nozzle 2, and therefore the lubrication nozzle 2 The oil ejected from the air, that is, the ejected state becomes unstable, but by providing the oil rectifier 14 as in the present embodiment, high-frequency noise is suppressed as shown in FIG. It can be seen that the oil to be ejected (that is, the noise F has disappeared) is stable and unnecessary reflected waves are suppressed. FIG. 8 shows a frequency spectrum.

Furthermore, according to the configuration of the present embodiment, a new driving device for generating a high pressure as in the electrohydraulic type is not required.
According to the configuration of the pressure wave oil feeding type cylinder lubrication device, when sending the lubricating oil to the lubricating oil supply pipe 12 between the oil feeder 11 and the lubricating oil supply pipe 12, a check valve function is provided. An oil pressurizer 13 capable of generating a pressure wave is provided, and a pressure wave pulsation is rectified by having a rectifying hole 51b capable of confining a pressure reflected wave of the lubricating oil guided through the lubricating oil supply pipe 12. Since the oil rectifier 14 is provided, the lubricating oil can be supplied to the lubricating nozzle 2 at a high pressure, so that the lubricating oil can be reliably jetted into the cylinder at a predetermined timing, that is, the lubricating oil can be injected.

  Further, the oil pressurizer 13 has a check valve function, that is, it is a mechanical type instead of an electrohydraulic type, and therefore has a simple and inexpensive configuration and is equivalent to an electrohydraulic type. Function can be demonstrated.

  Furthermore, since the oil rectifier 14 having the rectifying hole 51b is provided in front of the oil supply nozzle 2, the pressure wave that flows backward from the oil supply nozzle 2, that is, the reflected pressure wave is prevented from being transmitted to the lubricating oil supply pipe 12 side. Therefore, the pressure between the oil pressurizer 13 and the oil rectifier 14 can be stabilized, so that the pressure wave from the oil pressurizer 13 can be reliably guided to the oil supply nozzle 2 side.

  Incidentally, as shown in FIG. 9, in the oil pressurizer 13 described in the above embodiment, the first valve body 42 is made of steel (that is, made of a ferromagnetic material), and the pressurizer main body 41 is used. You may arrange | position the electromagnet 61 which makes a magnetic force line act on this 1st valve body 42 in the side.

Thus, by providing an electromagnet to turn on / off the holding current, that is, by controlling the electromagnetic force, the valve opening timing can be controlled with high accuracy.
Furthermore, as shown in FIG. 10, the inner diameter of the large-diameter hole portion 2 c of the oiling nozzle 2 may be gradually reduced toward the tip.

  Thus, the pressure of the lubricating oil can be further increased by gradually narrowing the lubricating oil passage downstream from the oil rectifier 14.

1 is a layout diagram of a schematic overall configuration of an oiling device according to an embodiment of the present invention. It is sectional drawing which shows the structure of the oil delivery device and oil pressurizer in the oil supply apparatus. It is sectional drawing which shows the principal part structure of the oil pressurizer. It is sectional drawing which shows the structure of the oil rectifier and oil supply nozzle in the oil supply apparatus. It is principal part sectional drawing which shows the ejection part of the oiling nozzle in the oiling apparatus. It is a wave form diagram which shows the pressure which generate | occur | produces with the oil pressurizer, and the pressure which generate | occur | produces on the oiling nozzle side. It is a wave form diagram which compares the pressure which generate | occur | produces with the oil pressurizer, and the pressure which generate | occur | produces with a mechanical lubrication apparatus. It is a wave form diagram of a pressure wave generated with the oil rectifier. It is sectional drawing which shows the principal part structure of the oil pressurizer which concerns on other embodiment of this invention. It is sectional drawing which shows the oiling nozzle which concerns on other embodiment of this invention. It is a layout of the schematic overall configuration of an oiling device according to a conventional example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder side wall part 2 Lubrication nozzle 3 Cylinder chamber 11 Oil delivery device 12 Lubricating oil supply pipe 13 Oil pressurizer 14 Oil rectifier 21 Reservoir tank 21a Side wall part 21b Hole part 22 Block body 22a Oil delivery hole part 23 Suction side check valve 24 discharge side check valve 25 oil supply device 26 cylindrical member 32 rocker arm 33 cam 41 pressurizer body 41a first oil hole portion 41b communication hole portion 41c second oil hole portion 42 first valve body 44 coil spring 51 Rectifier body 51a Oil introduction hole 51b Rectification hole 52 Second valve body 53 Coil spring

Claims (6)

A cylinder lubrication device that directs lubricating oil to a lubrication nozzle provided on a cylinder side wall of a diesel engine and injects the lubricant into a cylinder chamber,
An oil delivery section for delivering a predetermined amount of lubricating oil in synchronization with the rotation of the engine, a lubrication oil supply passage for supplying the lubrication oil sent from the oil delivery section to the lubrication nozzle, and a check valve function; An oil pressurizing unit that pressurizes the lubricating oil delivered from the oil delivery unit to generate a pressure wave and delivers the pressure wave to the lubricating oil supply path, and is disposed in front of the oiling nozzle and has a check valve function and the lubrication An oil pressure rectifier having a confining space that can confine pressure reflected waves of lubricating oil guided through an oil supply path and rectifying pressure wave pulsation Cylinder lubricator. A pressurizing unit main body in which an oil pressurizing unit is formed with a large-diameter first oil passage that guides lubricating oil from the oil delivery unit, and a small-diameter second oil passage communicating with the first oil passage; A first valve body arranged on the oil passage side and capable of opening and closing the opening of the first oil passage, and a first attachment capable of closing the opening by urging the first valve body toward the first oil passage. A force member,
A rectifying unit body in which a small-diameter third oil passage for guiding lubricating oil from a lubricating oil supply passage and a large-diameter fourth oil passage communicating with the third oil passage are formed, and the fourth oil A second valve body disposed on the passage side and capable of opening and closing the opening of the third oil passage, and a second urging force that urges the second valve body toward the third oil passage and closes the opening. The pressure wave oil supply type cylinder oil supply device according to claim 1, wherein the oil supply device is constituted by a member.   The size of the first valve body is such that the projected area of the first valve body with respect to the oil passage cross section is approximately five times as large as the opening area where the first valve body opens and closes. 2. Pressure wave oil feeding type cylinder lubrication device according to 2.   The first valve body is made of a magnetic material, and an electromagnet capable of urging the first valve body in the same direction as the urging direction of the first urging member is provided in the pressurizing portion main body. Item 4. A pressure wave oil feeding type cylinder lubricating device according to Item 2 or 3.   The pressure wave oil feeding type cylinder oiling device according to any one of claims 2 to 4, wherein an inside diameter of an oiling hole provided in the oiling nozzle is sequentially reduced toward the tip.   6. The jet nozzle formed at the tip of the oil supply nozzle is formed in such a direction that the jet direction is along the inner wall surface of the cylinder chamber and along the circumferential direction. Pressure oil supply type cylinder lubrication device as described in 1.

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