JP2009264302A - Lubricating oil supply device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating oil supply device provided with a backup means for a stoppage of drive of the device due to failure or the like, which can adjust an oil discharge amount depending on required amount, and moreover is of a simple structure that utilizes effectively a means for adjustment. <P>SOLUTION: A lubricating oil supply device 0100 is configured to include an operating lever 0130 for transmitting a reciprocating motion of a piston to a plunger, by swinging with the reciprocating motion of a piston 0112 swingably held about a shaft and a biasing force of a member 0123 for biasing the plunger 0122; and an eccentric cam 0140 for regulating a range of the reciprocating motion of the piston and plunger by being rotatably held near the operating lever and regulating a swing range of the operating lever, and even when the piston is stopped due to malfunction of a power source, for swinging the operating lever by continuously rotating to drive by another power source, and for driving the plunger to suck and deliver oil. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a lubricating oil supply device for preventing seizure and wear reduction of an internal combustion engine.

Regarding the lubricating oil supply device for preventing seizure of the cylinder and plunger (piston) constituting the internal combustion engine (engine) and reducing wear, lubrication is performed at an optimal timing without wasting the lubricating oil during discharge. There have been technologies to make it possible to do so. For example, Patent Document 1 discloses a lubrication pump system that enables lubrication in association with an engine cycle accurately by performing extrusion lubrication with a hydraulic cylinder controlled by an electromagnetic valve (see Patent Document 1).
Special table 2004-519595 gazette

  Incidentally, the required amount of lubricating oil discharged toward the engine may vary depending on the shape of the piston of the engine to be lubricated, the reciprocating speed of the piston, and the like. However, the conventional method cannot adjust the discharge amount of the lubricating oil according to the required amount.For example, although a smaller discharge amount is sufficient, an excessive amount of lubricating oil is discharged, and as a result There was a problem that the lubricant was wasted.

  In addition, when the drive of the lubricating oil supply device is stopped due to a failure or the like, the engine seizure and wear reduction will be prevented if the discharge of the lubricating oil stops even though the engine continues to drive. Will not be able to. Therefore, in order to avoid such a situation, a backup means for allowing the lubricant to be discharged manually is required. In that case, it is desirable that the backup means is provided with a mechanism that is unlikely to break down and can be provided at a low cost. For this purpose, a means provided for discharging the lubricating oil, which is an original function of the apparatus, is provided. A simple structure that is effectively used is required. However, no conventional apparatus has such a backup means.

  Therefore, the problem to be solved by the present invention is a lubricating oil supply device that can adjust the discharge amount of the lubricating oil according to the required amount, and thereby can suppress the discharge amount of the lubricating oil to the minimum necessary. In addition, it is an object of the present invention to provide a lubricating oil supply device having a simple structure that effectively uses the means for adjustment and provided with backup means when the drive of the device is stopped due to a failure or the like.

  In order to solve the above problems, the present invention provides a first pump comprising a first cylinder and a piston disposed in the first cylinder and reciprocating in the first cylinder in synchronization with the engine piston, A second cylinder provided with a suction port, a plunger disposed in the second cylinder, reciprocatingly moved in the second cylinder to discharge lubricating oil into the engine, and for urging the plunger in the oil suction direction A second pump composed of an urging member, and is configured to be swingably held about an axis so that one end can be driven as the end of the piston moves, and the other end is the end of the plunger as it moves The piston is reciprocated by the reciprocating motion of the piston and the urging force of the urging member to transmit the reciprocating motion of the piston to the plunger. A movable lever, which is provided in the vicinity of the operating lever, is rotatably held, and restricts the range of reciprocation of the piston and the plunger by restricting the swinging range of the operating lever. Even when the power source is stopped due to a malfunction of the power source or the like, the operation lever is swung by driving continuously with a power source different from the power source for reciprocating motion of the piston, and the plunger is driven to Provided is a lubricating oil supply device including an eccentric cam that enables suction and discharge of oil by a pump.

  According to the present invention, it is possible to adjust the discharge amount of the lubricating oil according to the required amount, and thereby the lubricating oil supply device that can suppress the discharge amount of the lubricating oil to the necessary minimum. Therefore, it is possible to provide a lubricating oil supply apparatus having a simple structure that effectively uses the means for the above-described purpose and provided with a backup means when the drive of the apparatus is stopped due to a failure or the like.

  Examples of the present invention will be described below. In addition, this invention is not limited to these Examples at all, and can be implemented in various modes without departing from the gist thereof.

<Overview>
The lubricating oil supply device of this embodiment is lubricated according to the required amount by an operating lever that is swingably held around an axis and an eccentric cam that is rotatably held and restricts the swing range of the operating lever. This is a lubricating oil supply device that can adjust the amount of oil discharged, and that can discharge lubricating oil using this operating lever and eccentric cam when the drive of the device stops due to failure or the like .

<Configuration>
(General)
FIG. 1 is a conceptual diagram showing an example of the configuration of a lubricating oil supply apparatus according to the present invention. First, the general configuration of the lubricating oil supply device of the present invention will be described with reference to this drawing. In addition, since this figure is a conceptual diagram to the last, it does not necessarily show the physical arrangement position, shape, dimension, etc. of each component in an actual system.

  As shown in the figure, the “lubricating oil supply device” 0100 of this example includes a “first pump” 0110, a “second pump” 0120, an “actuating lever” 0130 (shown by diagonal lines), and an “eccentric cam”. "0140". This figure is a vertical sectional view cut at a substantially central portion of the first pump and the second pump. In the example of this figure, the operating lever is swingable on a shaft 0131 provided in the tank in an “oil storage tank” 0150 for storing lubricating oil 0101 (hereinafter sometimes simply referred to as “oil”). The oil is sucked into the second cylinder body from the oil storage tank through the “oil suction port” 0124 provided in the “second cylinder” 0121 of the second pump. . Note that the oil storage tank is not an essential component of the lubricating oil supply device of the present invention.For example, the lubricating oil stored in the oil storage tank, which is the external device of the lubricating oil supply device, is supplied from an oil suction port via a pipe or the like. It may be configured to inhale into the second cylinder. The oil sucked into the second cylinder is discharged to a lubrication target (for example, a piston ring) in an engine (not shown) located above the second cylinder in this drawing.

(First pump)
(General)
The “first pump” is a pump for driving the lubricating oil supply device, and includes a “first cylinder” 0111 and a “piston” 0112.

(piston)
The piston is disposed in the first cylinder, and is configured to reciprocate in the first cylinder in synchronization with the engine piston. In addition, since reciprocating motion synchronized with the engine piston can be realized using a known technique, description thereof is omitted here.

  The lubricating oil supply device is driven by transmitting a driving force such as a motor (not shown) to the piston of the first pump to reciprocate the piston in the first cylinder. , By sequentially transmitting to the plunger of the second pump. As a result, the plunger of the second pump reciprocates in the second cylinder, and the lubricating oil is discharged to the lubrication target in the engine. At this time, since the reciprocating motion of the piston of the first pump is synchronized with the engine piston as described above, the oil is discharged to the lubrication target of the engine at the optimum timing.

  The type of power source for driving the piston of the first pump is not limited. For example, pneumatic control or hydraulic control may be used in addition to the above-described motor from the viewpoint of noise prevention.

  A specific configuration for enabling the driving force of the piston synchronized with the engine piston to be sequentially transmitted to the operating lever and the plunger will be described later in the configuration of the operating lever.

(Second pump)
(General)
The “second pump” includes a “second cylinder” 0121, a “plunger” 0122, and an “urging member” 0123.

(Second cylinder)
The second cylinder is for causing the plunger to reciprocate inside to discharge oil into the engine. In the example of FIG. 1, oil is discharged from an oil discharge port 0121a provided at the upper end of the second cylinder into an engine (not shown) positioned above the oil discharge port 0121a. In the second cylinder, it is desirable to provide a check valve 0121b as shown in the example of this figure in order to prevent a reverse flow (flow from the oil discharge port side to the suction port side) during oil suction. .

  The second cylinder is provided with an “oil suction port” 0124 as described above. The suction port is a port for sucking oil stored in the oil storage tank into the second cylinder. There is no particular limitation on the shape and structure of the mouth. The oil suction port shown in the figure has a cylindrical shape, and sucks oil from the opening 0124a at the tip thereof, and feeds the oil into the second cylinder through the tubular portion 0124b provided inside. This is an example of In this case, a check valve 0124c is provided in a part of the tubular portion as shown in the example of this figure in order to prevent a back flow (flow from the second cylinder main body side to the suction port opening side) during oil discharge. It is desirable.

(Plunger)
The plunger is arranged in the second cylinder, and is configured to reciprocate in the second cylinder to discharge the lubricating oil into the engine. This reciprocation of the plunger is performed by the driving force transmitted from the piston of the first pump through the operating lever. A specific configuration for enabling transmission of the driving force synchronized with the engine piston from the operating lever to the plunger will also be described in the configuration of the operating lever described later.

(Biasing member)
The biasing member is for biasing the plunger in the oil suction direction. Here, the “oil suction direction” literally means the direction in which oil is sucked, in other words, the direction opposite to the direction toward the oil discharge port. In the example of this figure, the urging member urges the plunger in the downward direction, which is the direction opposite to the direction (upward direction) toward the oil discharge port 0121a. The urging member in this figure is an example of a spring, but the type of the urging member is not limited to this, and may be, for example, rubber or another elastic body.

  This urging member is necessary so that, when the piston of the first pump moves up, one end of the operating lever follows and lifts up. More specifically, since the urging member always urges the plunger downward, the plunger pushes down the other end of the operating lever when the piston of the first pump moves up, thereby the operating lever. Is pushed up. The specific operation of this urging member will also be described later in the configuration of the operating lever.

(Operating lever)
The “actuating lever” is swingably held around a shaft 0131 (the shaft attached to the oil storage tank in the example of FIG. 1), and is configured such that one end 0132 can be driven as the piston end portion 0112a moves. The other end 0133 is configured to be able to drive the end portion 0122a of the plunger as it moves, and is oscillated by the reciprocating motion of the piston and the urging force of the urging member, thereby transmitting the reciprocating motion of the piston to the plunger. Is configured to do.

  As described above, the plunger is always urged downward in the drawing by the urging member, and a force to push down the other end of the operating lever acts. By the action of a force that pushes down the other end of the actuating lever, a force that pushes it upward is always applied to one end of the actuating lever that is swingably held around the shaft.

  In the process of reciprocating the piston, when the piston moves down, the force that the piston tries to move down collides with the force that the end of the operating lever lifts up. Since the driving force of the motor or the like is set so as to exceed the force, the piston moves downward. As a result, one end of the operating lever is also pushed down, and the other end of the operating lever that swings about the shaft is pushed up. At this time, the force at which the other end of the actuating lever lifts and the force at which the plunger moves downward by the urging member collide with each other, but the driving force of the motor or the like so that the former force is exceeded. Is set, the other end of the actuating lever is lifted, and the plunger is moved upward accordingly.

  On the contrary, when the piston moves upward, the force that the piston tries to push down one end of the operating lever does not work. Accordingly, the force at which the other end of the operating lever is lifted by the driving force from the piston does not work, and the other end of the operating lever is pushed down by the biasing force of the plunger. That is, since the plunger moves downward and the other end of the operating lever is pushed down as the plunger moves, the one end of the operating lever is pushed up following the upward movement of the piston.

  With the configuration as described above, the operating lever is swung by the reciprocating motion of the piston synchronized with the engine piston, and the plunger reciprocates so that oil can be discharged at the optimal timing synchronized with the engine piston. .

  In FIG. 1, the operating lever is attached at a position where it is completely buried in the oil, and the contact between the piston end portion 0112a of the first pump and the end portion 0132 of the operating lever, and the end portion of the plunger of the second pump. The contact between 0122a and the other end 0133 of the actuating lever is shown so that it is always immersed in oil (the eccentric cam 0140, which will be described later, and the projection 0134 provided slightly inside the one end of the actuating lever). The same applies to contacts). However, this is not essential. If the opening 0124a at the tip of the oil suction port of the second cylinder is immersed in the oil so that the oil can be sucked in, the remaining components are immersed in the oil. It does not have to be. However, from the viewpoint of preventing wear of each member due to friction between contacting components, the contact between the end of the piston and one end of the actuating lever is always immersed in oil as in this example. Is desirable.

  Furthermore, in the above description, the example in which the reciprocating motion of the piston and the plunger and the swinging of the operation lever are in the vertical direction (vertical direction) has been described. However, this is not essential. It is also possible to arrange the members so as to be in the front-rear direction or the left-right direction (the same applies to the following description).

(Specific configuration for transmission of driving force from the piston to the plunger via the operating lever)
Next, in order to show the point of how oil is discharged toward the engine by the reciprocating motion of the piston, the swing of the operating lever and the reciprocating motion of the plunger as described above, it is operated from the piston while using another figure. An example of a specific configuration for transmitting the driving force to the plunger via the lever will be described in a transitional manner.

  2 to 4 are diagrams for explaining an example of a specific configuration for transmitting the driving force from the piston to the plunger via the operating lever, and the state of transmission is continued from the state of FIG. It is shown in transition in the order of the figure numbers as time passes.

  The state of FIG. 1 shows a state in which the piston is driven and moved to the lowest position in the first cylinder. In this state, one end of the operating lever is also pushed down by the end of the piston and moved to the lowest position. Further, along with this, the other end of the operating lever is moved to the uppermost position. For this reason, the other end of the operating lever pushes the plunger up to the uppermost position in the second cylinder, and the discharge of oil by the plunger is completed.

  FIG. 2 shows a state in which the piston 0212 has moved slightly upward in the first cylinder 0211 from the state of FIG. In this state, one end 0232 of the operating lever 0230 follows the piston 0212 by the urging force of the urging member 0223 and moves slightly above the lowest position, and the other end 0233 of the operating lever is slightly below the uppermost position. It will be in the state moved to. At this time, the plunger 0222 is moved from the uppermost position in the second cylinder 0221 to a position slightly below by the urging force of the urging member, and the oil is sucked into the second cylinder.

  FIG. 3 shows a state where the piston 0312 further moves up in the first cylinder 0311 from the state shown in FIG. 2 to the uppermost position. In this state, one end 0332 of the operating lever 0330 is further moved to the uppermost position by following the piston by the urging force of the urging member 0323, and the other end 0333 of the operating lever is moved to the lowermost position. . At this time, the plunger 0322 is moved to the lowest position in the second cylinder 0321 by the urging force of the urging member, and the suction of the oil into the second cylinder is completed.

  FIG. 4 shows a state where the piston 0412 has moved a little downward in the first cylinder 0411 from the state of FIG. In this state, due to the downward movement of the piston, one end 0432 of the operating lever 0430 is also pushed down to a slightly lower position. For this reason, the other end 0433 of the operating lever also moves to a slightly higher position, and is pushed up to move the plunger 0422 to a slightly higher position, so that the oil in the second cylinder 0421 is being discharged. . Thereafter, the piston moves further downward, and again completes the oil discharge as shown in FIG. 1, and this cycle is repeated thereafter.

(Configuration to discharge oil to multiple lubrication objects at once)
In the above, the configuration for discharging the lubricating oil to a single lubrication target by the combination of a pair of the first pump, the second pump, the operation lever, etc. has been described, but the lubricating oil supply device of the present embodiment is By providing a plurality of such combinations, it is also possible to discharge the lubricating oil to a plurality of lubrication objects at once. In FIG. 1, only a combination of the first pump, the second pump, the operating lever, and the like is shown in the vertical cross-sectional view, but another set of similar combinations is present in front and / or behind the combination. The configuration in which is connected is also included in the concept of the lubricating oil supply device shown in FIG.

  In that case, the first pump, the second pump, the operating lever, etc. may not necessarily be provided individually for each lubrication target. For example, the driving force is transmitted to all the second pumps with one common operating lever. There may be a component used in common by a plurality of groups.

FIG. 5 is a diagram illustrating an example of a configuration of a lubricating oil supply apparatus capable of collectively discharging oil to a plurality of lubrication targets.
Among these, Fig.5 (a) is a top view which shows an example of this lubricating oil supply apparatus, and shows the state which looked at the apparatus shown in FIG. 1 from the top. In the lubricating oil supply apparatus shown in the figure, a single oil storage tank 0550 is provided with a plurality of sets each including a first pump 0510, a second pump 0520, and an operating lever 0530 (shown by hatching). Only one set is shown to avoid it). Moreover, in the example of this figure, these several actuating levers are hold | maintained centering on one axis | shaft 0531 (the range enclosed with the broken line is shown) which is common.

FIG. 5B is a cross-sectional view taken along the line AA of FIG. 1, that is, a state in which the actuator is cut by a vertical cross section penetrating substantially the center of the operating lever shaft in the axial direction. Also in this drawing, a state is shown in which a plurality of operating levers 0530 are held around a common shaft 0531.
If the lubricating oil supply apparatus as shown in this figure is used, for example, a plurality of first pumps, second pumps, and a plurality of pistons that reciprocate in synchronization with the respective engines with respect to the lubrication targets of the plurality of engines. Lubricating oil can be discharged at an optimal timing for each lubrication target by collectively driving a set of operating levers.

  Further, among the plurality of sets such as the first pump, the second pump, and the operating lever of the lubricating oil supply apparatus capable of collectively discharging oil to a plurality of lubrication objects, only a part of the plurality of sets is driven to drive a plurality of sets. It is also possible to supply oil to only a part of the lubrication target. A specific example of such a configuration will be described later as another embodiment.

(Eccentric cam)
Next, returning to FIG. 1, the configuration of the eccentric cam will be described.
The “eccentric cam” 0140 is provided in the vicinity of the operation lever 0130, is rotatably held, and restricts the range of reciprocation of the piston 0112 and the plunger 0122 by restricting the swing range of the operation lever. Even when the piston is stopped due to a malfunction of the power source, etc., the operating lever is swung by driving continuously with a power source different from the power source for reciprocating movement of the piston, and the plunger is driven to The oil can be sucked and discharged by two pumps.

(Configuration for regulating the swing range of the operating lever)
One function of the eccentric cam is to regulate the range of reciprocation of the piston and plunger by regulating the swing range of the actuating lever. This aims at making the discharge amount adjustable while maintaining the same timing of oil discharge from the second cylinder.

  FIG. 6 is an enlarged view of the eccentric cam and the vicinity thereof. The eccentric cam 0640 shown in the figure is provided in the form of being directly attached to the oil storage tank 0650 in the vicinity of the operation lever 0630, and is held rotatably about the shaft 0641. Here, “rotatable” means that the eccentric cam can be rotated and fixed in an arbitrary direction, and does not mean that the eccentric cam always rotates during the reciprocating motion of the piston. That is, after the eccentric cam is fixed in an arbitrary direction, unless the eccentric cam is rotated again to change the discharge amount in order to change the discharge amount, the eccentric cam is set in the fixed direction. The piston motion is continued in a fixed state, and oil discharge is repeated (except when an eccentric cam is used as backup means in the event of a failure described later).

Thus, by providing the eccentric cam in the vicinity of the operating lever, the swinging range of the operating lever is restricted to a range in which the operating lever does not rise to the right from the state in which the operating lever is in contact with the lower end of the eccentric cam. FIG. 6 shows the same state as FIG. 1, that is, the state where the operating lever is at the lowest right. On the other hand, although the enlarged view is omitted, FIG. 3 described above shows a state in which the operating lever is raised to the rightmost, and the projection 0334 provided slightly inside one end of the operating lever is in contact with the lower end of the eccentric cam. Even if the piston 0312 moves further upward from this state, the operating lever is restricted by the eccentric cam and cannot be lifted further to follow the movement of the piston.
From the above, the operating lever can swing between the lowermost position shown in FIG. 6 (FIG. 1) and the uppermost position shown in FIG.

  The operation of rotating the eccentric cam and fixing it at an arbitrary position may be performed manually, for example. FIG. 6 is an example in which the lower end of the eccentric cam is fixed to the uppermost position as in FIGS. 1 to 4 (not shown clearly in this figure, but shown in the next FIG. 7A). As shown in the figure, the eccentric cam 0740 can rotate around the axis in a virtual circle drawn around the eccentric cam 0740, and the eccentric cam shown in FIG. 6 is located at the top of the virtual circle. Shown). Accordingly, the swing range of the operating lever is maximized in the state shown in this figure. If the eccentric cam is rotated 180 degrees around the axis from the state shown in these figures and fixed so that the lower end of the eccentric cam is at the lowest position, the swing range of the operating lever is minimized.

7A and 7B are diagrams showing an example in which the swing range of the operating lever is changed by rotating the eccentric cam together with FIG. 1 described above.
As described above, FIG. 1 is an example in which the eccentric cam is fixed so that the lower end of the eccentric cam is at the uppermost position, and the swing range of the operating lever is maximized. In this case, since the reciprocating amount of the plunger is also maximized, the oil suction amount and the discharge amount are also maximized. Therefore, the eccentric cam may be fixed in such a direction when it is desired to maximize the oil discharge amount.

  FIG. 7A is an example in which the eccentric cam 0740 is fixed in a state of being rotated 90 degrees in the virtual circle from the state of FIG. In this case, the lower end of the eccentric cam moves to a slightly lower position as compared with FIG. 1, so that the swing range of the operating lever 0730 becomes relatively small. Therefore, the amount of oil sucked and discharged is relatively small.

  FIG. 7B shows an example in which the eccentric cam 0740 is fixed in a state rotated by 90 degrees from the state shown in FIG. 7A. In this case, since the lower end of the eccentric cam moves to the lowest position, the swing range of the operating lever 0730 is minimized, and the oil suction amount and the discharge amount are also minimized. Therefore, when it is desired to minimize the oil discharge amount, the eccentric cam may be fixed in such a direction.

  Thus, the amount of oil discharged can be increased or decreased by rotating the eccentric cam and changing the direction, but the oil discharge timing does not change at this time. This is because even if the direction of the eccentric cam is changed, the reciprocating period of the piston, the swinging period of the operating lever, and the reciprocating period of the plunger do not change. More specifically, as is clear from the examples of FIGS. 1, 7A, and 7B, even if the direction of the eccentric cam is changed, the period of the piston that reciprocates in synchronization with the engine piston does not change. There is no change in the oscillation cycle of the actuating lever driven by this. However, since the uppermost position of one end of the actuating lever changes due to the change in the lower end position of the eccentric cam, while the lowermost position of one end of the actuating lever does not change, only the amplitude of the actuating lever changes. For this reason, the reciprocating motion of the plunger that constantly urges the other end of the operating lever also changes the reciprocating motion distance without changing the cycle. Thereby, it becomes possible to adjust only the discharge amount as needed while maintaining the discharge of oil synchronized with the engine piston.

  In addition, as described above, the lubricating oil supply device of the present embodiment can be configured so that the lubricating oil can be discharged collectively to a plurality of lubrication objects, but the configuration of the eccentric cam in this case also In addition, an eccentric cam may be individually provided together with the first pump, the second pump, and the operation lever for each lubrication target. For example, the swing range of all the operation levers may be regulated by one common eccentric cam. An eccentric cam common to a plurality of sets may be provided.

  FIG. 5C is a cross-sectional view taken along the line BB in FIG. 1, that is, a state in which the eccentric cam is cut along a vertical cross section penetrating substantially the center of the shaft in the axial direction. In the example of this figure, the state where the one cylindrical eccentric cam 0540 for restricting the rocking | fluctuation range of several actuating lever 0530 collectively is appearing.

  In addition to this, there are various variations in the shape and mounting procedure of the eccentric cam. For convenience, this variation will be described in the description when the next piston is stopped due to a failure or the like.

(Configuration for swinging the operating lever when the piston is stopped)
Another function of the eccentric cam is that even if the piston is stopped due to a malfunction of the power source, the operating lever is swung by continuously rotating it with a power source different from the power source for the reciprocating motion of the piston. Then, the plunger is driven to enable the oil to be sucked and discharged by the second pump. In the present invention, the eccentric cam has a simple structure that effectively utilizes the structure provided for the actual function as described above, and the oil is discharged by turning this manually. We are trying to continue.

  FIG. 8 is a diagram illustrating an example of a configuration for rotationally driving a cam by another power source, and is a perspective view illustrating an example of an appearance of a lubricating oil supply device including such an eccentric cam. . This figure is an example in which a set of a first pump 0810, a second pump 0820, and an operating lever (not shown) is provided in the oil storage tank 0850. A handle shaft 0860 that coincides with the axis of the eccentric cam 0840 for restricting the swing range of the operating lever is attached, and a handle 0861 is provided at the tip of the handle shaft 0860. By rotating the handle by hand, the eccentric cam is pivoted. It can be rotated around the center. When the power source breaks down, the handle is rotated by hand to rotate the eccentric cam, thereby swinging the operating lever using the movement of the eccentric cam and the urging force of the urging member, and reciprocating the plunger. The oil can be discharged by exercising.

  FIG. 9 is a diagram showing another example of a configuration for rotationally driving a cam by another power source. This figure is an example in which a set of a first pump 0910, a second pump 0920 and an operating lever is provided in the oil storage tank 0950, as shown in FIG. Unlike the example, this is an example of a lubricating oil supply apparatus provided with a plurality of such oil storage tanks. The example in this figure assumes that each set of pistons is driven by a separate power source. When some of these power sources fail, a set of eccentric cams corresponding to the failed power source is provided, for example, on the worm 0962 and the eccentric cam provided on the handle shaft 0960 as shown in this figure. The eccentric cam may be rotated by turning the handle 0961 provided at the tip of the handle shaft by hand using a worm gear comprising the worm wheel 0963. Accordingly, in this case, the operation lever can be swung using the movement of the eccentric cam and the urging force of the urging member, and the plunger can be reciprocated to discharge the oil.

  Furthermore, FIG. 10 is also a diagram showing another example of the configuration for rotationally driving the cam by another power source. In this figure, as in the example shown in FIG. 5 (c), a set of a plurality of first pumps 1010, second pumps 1020 and operating levers (not shown) is provided in one oil storage tank 1050. FIG. 5 shows an example in which one substantially cylindrical eccentric cam 0840 is held to collectively control the swing range of the plurality of operating levers (however, in order to avoid complications, (The illustration of the number of groups shown in FIG. 5 (c) is partially omitted, and only one group is shown). In the example of this figure, a handle shaft 1060 that matches the axis of the eccentric cam is attached, and a handle 1061 is provided at the tip thereof. The example in this figure assumes that each set of pistons is driven by one power source. Therefore, if the power source fails, for example, by rotating the handle by hand, the eccentric cam is rotated around the shaft, and all the operating levers are swung together to reciprocate all the plungers. Can be made.

  Although not shown in this figure, the eccentric cam of this example does not have a uniform cross-section (for example, a circle with the same diameter), but includes a plurality of cams with different cross-sections that are often found on engine camshafts. It may have a shape like a chain. In this case, it is possible to discharge oil at different timings for each lubrication target while keeping the same period of reciprocation of each plunger.

  Or although illustration is abbreviate | omitted, when several 1st pumps and 2nd pumps are provided in one oil storage tank like FIG. 10, only one actuating lever is provided and one eccentric cam The plurality of plungers may be driven in a lump by rotating the actuator lever. In this case, for example, it is conceivable that the operating lever has a fan shape that spreads toward the plunger side. Then, an eccentric cam provided at the main position of the fan (thus, it may be a short cylindrical shape instead of the long cylindrical shape as shown in FIG. 10) is rotated by a handle to swing the fan-shaped operating lever. A plurality of plungers that are in contact with each other at substantially the tip position may be collectively driven.

  In the above description, the power source other than the power source for the reciprocating motion of the piston has been described as an example in which the power source is manual. However, this other power source may be a motor provided separately from the piston power source. It may be. When the other power source is a motor, it is possible to drive in synchronism with the engine piston in the same way as the power source of the piston, and the oil can be discharged at the optimal timing that is no different from when there is no failure. It becomes possible. On the other hand, in the case of manual operation, as is clear from the examples shown in FIGS. 8 to 10, there is an advantage that the backup means can be provided with a very simple structure as compared with the case where another motor is provided.

  In addition, in the case of manual operation, it is difficult to discharge oil at an optimal timing that is the same as when there is no failure. However, lubricating oil is supplied to engine pistons that require lubrication in a timely manner. There is no change in that we can continue. In addition, there is no change in that the backup means can be provided with a structure that effectively uses an eccentric cam that is a means for adjusting the discharge oil amount according to the required amount. Therefore, this manual backup means is included. The present invention solves the common technical problem of providing a lubricating oil supply device capable of adjusting the amount of discharged oil according to the required amount, and has the unity of the invention. Needless to say.

<Effect>
According to the invention of the present embodiment, it is possible to adjust the discharge amount of the lubricating oil according to the required amount, and thereby the lubricating oil supply device capable of suppressing the discharge amount of the lubricating oil to the necessary minimum, It is possible to provide a lubricating oil supply device having a simple structure that effectively uses the means for adjustment and provided with backup means when the drive of the apparatus is stopped due to a failure or the like.

<Overview>
The lubricating oil supply device of the present embodiment is configured so that the lubricating oil can be discharged collectively to a plurality of lubrication objects by having a plurality of combinations of the first pump, the second pump, the operating lever, and the like. In particular, the present invention is characterized in that only a part of the plurality of sets is driven to supply oil to only a part of the plurality of lubrication objects.

<Configuration>
(General)
FIG. 11 is a conceptual diagram showing an example of the configuration of the lubricating oil supply device of the present embodiment. The lubricating oil supply apparatus shown in this figure has two sets of first pumps 1110a, 1111b, and eight sets of second pumps 1120a1, 1120a2, 1120a3, 1120a4, 1120b1, 1120b2, 1120b3, 1120b4. Further, the lubricating oil supply device of this figure is also provided with operating levers 1130a and 1130b similar to the device described in the first embodiment, and the reciprocating motion of the pistons 1112a and 1112b of the first pump is performed via this operating lever. Pump plungers 1122a1, 1122a2, 1122a3, 1122a4, 1122b1, 1122b2, 1122b3, and 1122b4 are transmitted to the engine cylinder 1170 disposed above the second pump in this figure by the reciprocating motion of the plunger. It is like that. The engine cylinder in this figure is a schematic plan view of an engine cylinder having a structure in which an engine piston reciprocates up and down in a substantially cylindrical cylinder. Further, eight engine side discharge ports 1170a1, 1170b1, 1170a2, 1170b2, 1170a3, 1170b3, 1170a4, 1170b4 are provided on the side surface of the engine cylinder at approximately 45 degree intervals.

  Further, in the lubricating oil supply apparatus of this figure, the first pump 1110a is replaced with four second pumps 1120a1, 1120a2, 1120a3, 1120a4, and the first pump 1110b is replaced with four second pumps 1120b1, 1120b2, 1120b3, 1120b4. For example, by driving the first pump 1110a, the four second pumps 1120a1, 1120a2, 1120a3, 1120a4 are driven via the operating lever 1130a, and the four pumps included in each second pump are provided. By reciprocating movement of the plungers 1122a1, 1122a2, 1122a3, and 1122a4, oil is discharged to the lubrication target (for example, piston ring) in the engine cylinder. The same applies to the first pump 1110b.

  That is, the lubricating oil supply apparatus shown in the figure drives only one of the two first pumps, supplies oil only from the corresponding four second pumps, and stops the other. The oil is not supplied from the remaining four second pumps corresponding to the first pumps.

  The lubricating oil supply apparatus according to the present embodiment is useful when, for example, driving a ship engine at a low speed or driving only a part of a plurality of engines during low-speed navigation of the ship. This is because in such a case, if the lubricating oil supply device of this embodiment is used, only a part of the first pumps are driven, and the oil is supplied only from the corresponding second pumps. This is because it is possible to further reduce the amount of oil discharged.

(Specific configuration of the first pump, second pump, etc.)
Next, according to the example of this figure, an example of specific structures, such as a 1st pump of a lubricating oil supply apparatus of a present Example, a 2nd pump, is demonstrated.

  In the example of this figure, there is one engine cylinder to be lubricated, and oil discharged from each of the eight second pumps is provided at eight locations in the engine cylinder corresponding to these eight second pumps. It is discharged from the engine side discharge port.

  Specifically, oil is discharged into the engine by the reciprocating motion of the plungers 1122a1, 1122a2, 1122a3, and 1122a4 of the second pump by the driving force transmitted from the first pump 1110a on the left side of the figure. It is performed from four engine-side discharge ports 1170a1, 1170a2, 1170a3, 1170a4 provided at intervals of approximately 90 degrees. On the other hand, the oil discharged into the engine due to the reciprocating motion of the plungers 1122b1, 1122b2, 1122b3, and 1122b4 by the driving force transmitted from the first pump 1110b on the right side of the figure is approximately halfway between the engine-side discharge ports. The four engine-side discharge ports 1170b1, 1170b2, 1170b3, and 1170b4 are provided so as to be positioned at intervals of approximately 90 degrees. As a result, in this example, oil is discharged into the cylinder from eight discharge ports arranged at approximately 45 ° intervals around the piston that reciprocates in the engine cylinder.

  Therefore, for example, when the engine is rotated at a low speed, only the left first pump 1110a is driven, and the engine cylinders are reciprocated by the corresponding reciprocating motions of the four second pump plungers 1122a1, 1122a2, 1122a3, 1122a4. It is sufficient to discharge oil. In this case, oil is discharged from only four engine-side discharge ports 1170a1, 1170a2, 1170a3, and 1170a4 that are arranged at intervals of about 90 degrees.

  By doing in this way, the quantity of lubricating oil which should be supplied with respect to the engine piston reciprocating at low speed can be reduced compared with when reciprocating at high speed. If the discharge amount from each second pump is the same as when the engine is rotating at high speed and the discharge from the eight second pumps is simply switched to the discharge from the four second pumps, the discharge amount Will be half of that at high speed.

  Alternatively, in the above case, the amount of oil discharged from each second pump may be slightly increased as compared with that during high-speed rotation. Such adjustment of the discharge amount can be realized by using the configuration for adjusting the discharge amount described in the first embodiment. As a result, the total amount of oil discharged from the four second pumps is slightly larger than half of that at the time of high speed rotation.

  In this case, the oil discharged from the four engine-side discharge ports 1170a1, 1170a2, 1170a3, 1170a4 penetrates into the gap between the piston and the cylinder and spreads as compared with the case where the discharge amount from each second pump is not increased. As the degree increases, it becomes possible to spread the oil over more surfaces of the object to be lubricated, for example, the piston ring. As a result, the seizure and wear of the engine piston can be appropriately prevented, and the amount of oil discharged can be further reduced as compared with the case where all the first pumps are driven.

  From this point of view, it is desirable that the positions where the engine-side discharge ports are provided be such that the discharge ports corresponding to the first pumps that are driven separately are alternately arranged. In FIG. 11, the engine side discharge ports 1170a1, 1170a2, 1170a3, 1170a4 corresponding to the first pump 1110a and the engine side discharge ports 1170b1, 1170b, 1170b3, 1170b4 corresponding to the first pump 1110b are spaced approximately 45 degrees. This is a preferable example of being alternately arranged.

  Similarly to the apparatus of the first embodiment, the lubricating oil supply apparatus of the present embodiment is continuously operated by a power source different from the power source for the reciprocating motion of the piston when the piston is stopped due to a malfunction of the power source. It can be configured such that the operation lever is swung by being driven to rotate, and the plunger is driven to enable the suction and discharge of oil by the second pump. The specific configuration for this purpose is the same as that described in the first embodiment, and a description thereof will be omitted.

(Other configuration examples)
Note that the configuration shown in FIG. 11 is merely an example, and only a part of the plurality of sets is driven and the oil is supplied to only a part of the plurality of lubrication objects by other configurations. It is possible. For example, unlike the example of FIG. 11, the first pump may be provided with a number corresponding to the second pump on a one-to-one basis. Further, in the example of FIG. 11, two actuating levers are provided corresponding to the first pump on a one-to-one basis, and each actuating lever is configured to transmit driving force to each of the four second pumps. However, unlike this, a total of eight may be provided in a form corresponding to the second pump on a one-to-one basis.

  Further, the engine cylinder to be lubricated may be configured to discharge oil to a plurality of engine cylinders instead of one as shown in FIG. If comprised in this way, when only a part is driven among several engine pistons, it will become possible to supply oil only to the engine cylinder of the driving engine piston. For example, slightly changing the example of FIG. 11, two engine cylinders are provided on the left and right, the four left second pumps are directed toward the left engine cylinder, and the four right second pumps are on the right side. An example in which oil is discharged toward the engine cylinder can be considered. In this case, when the right engine piston is stopped and only the left engine piston is driven, only the left first pump is driven to reciprocate only the plungers of the four left second pumps. It becomes possible to discharge oil only to the left engine cylinder. Also in this case, if there is no change in the discharge amount from each of the second pumps as compared with the case of discharging to both engine cylinders, the entire discharge amount can be halved.

<Effect>
According to the invention of the present embodiment, there is provided a lubricating oil supply apparatus configured to discharge a lubricating oil collectively to a plurality of lubrication objects by having a plurality of combinations of a first pump, a second pump, an operation lever, and the like. Among them, in particular, only a part of the plurality of sets is driven to supply oil to only a part of the plurality of lubrication objects, thereby reducing the discharge amount of the lubricating oil to a necessary minimum. It is possible to provide a lubricant supply device that can be used.

The conceptual diagram which shows an example of a structure of the lubricating oil supply apparatus which concerns on this invention The figure for demonstrating an example of the specific structure for transmission of the driving force from a piston to a plunger via an action lever. The figure for demonstrating an example of the specific structure for transmission of the driving force from a piston to a plunger via an action lever. The figure for demonstrating an example of the specific structure for transmission of the driving force from a piston to a plunger via an action lever. The figure which shows an example of a structure of the lubricating oil supply apparatus which can discharge oil collectively to several lubrication object Enlarged view of the eccentric cam and its vicinity The figure which shows the example which changed the rocking | fluctuation range of the actuating lever by rotating the eccentric cam The figure which shows the example which changed the rocking | fluctuation range of the actuating lever by rotating the eccentric cam The figure which shows an example of the structure for the rotational drive of the cam by another power source The figure which shows an example of the structure for the rotational drive of the cam by another power source The figure which shows an example of the structure for the rotational drive of the cam by another power source The conceptual diagram which shows an example of a structure of the lubricating oil supply apparatus of Example 2. FIG.

Explanation of symbols

0100 Lubricating oil supply device 0101 Oil 0110 1st pump 0111 1st cylinder 0112 Piston 0120 2nd pump 0121 2nd cylinder 0121a Oil discharge port 0121b Check valve 0122 in the 1st cylinder Plunger 0123 Energizing member 0124 Oil suction port 0124a Opening portion 0124b of oil suction port tubular portion 0124c of oil suction port Check valve 0130 in oil suction port Actuator lever 0131 Actuator lever shaft 0132 Actuation lever one end 0133 Actuation lever other end 0134 Actuation lever one end Protrusion 0140 Eccentric cam 0150 Oil storage tank provided slightly inside

Claims (1)

A first cylinder;
A piston disposed in the first cylinder and reciprocating in the first cylinder in synchronization with the engine piston;
A first pump consisting of
A second cylinder with an oil inlet,
A plunger that is disposed in the second cylinder and reciprocates in the second cylinder to discharge lubricating oil into the engine;
A biasing member for biasing the plunger in the oil suction direction;
A second pump comprising:
It is held swingably around the axis,
One end is configured to be drivable as the end of the piston moves,
The other end is configured to drive the end of the plunger as it moves,
An operating lever that transmits the reciprocating motion of the piston to the plunger by swinging with the reciprocating motion of the piston and the urging force of the urging member;
It is provided in the vicinity of the operating lever and is held rotatably.
By restricting the range of reciprocation of the piston and the plunger by restricting the swing range of the operating lever,
Even when the piston is stopped due to a power source malfunction or the like, the operating lever is swung by continuously driving the power lever different from the power source for the reciprocating motion of the piston, and the plunger is driven. An eccentric cam that enables suction and discharge of oil by the second pump,
Lubricating oil supply device comprising:

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