JP6693443B2 - Lubricating device for internal combustion engine - Google Patents

Description

  The present invention relates to a lubricating device for an internal combustion engine, and more particularly, to a lubricating device for an internal combustion engine having an oil jet that injects oil into a piston.

  A lubricating device for an internal combustion engine having an oil jet that cools a piston is disclosed in, for example, Japanese Patent Laid-Open No. 3-168317 (Patent Document 1).

  Patent Document 1 discloses a configuration in which an ECU (engine control unit) controls opening and closing of two electromagnetic valves connected to an oil jet. The opening and closing of the two solenoid valves is controlled by the engine speed and the piston position.

JP-A-3-168317

  In Patent Document 1, it is necessary to control the opening / closing timing of the electromagnetic valve by the ECU according to the position of the piston and at different valve timing for each cylinder. Therefore, there is a problem that the control signal becomes complicated, the calculation load increases, and the electronic wiring becomes complicated. Further, since the oil is always injected when the engine has a high rotation speed, there is a problem that the amount of work of the oil pump is large and the fuel efficiency is deteriorated.

  Therefore, the present invention has been made to solve the above-mentioned problems, and it is possible to control an oil jet with a simple configuration and to reduce the work amount of an oil pump that supplies oil to the oil jet. An object of the present invention is to provide a lubricating device for an internal combustion engine, which can reduce the fuel consumption and improve the fuel consumption.

  A lubricating device for an internal combustion engine according to the present invention includes a piston that is connected to a connecting rod and reciprocates, an oil jet that is supplied with oil from an oil pump and injects oil from the connecting rod side to the piston, and a phase of the piston. A permanent magnet that moves in response to the permanent magnet and a control unit that opens and closes the oil passage by a magnetic action with the permanent magnet according to the distance from the permanent magnet are provided. The oil is injected into the piston and the control unit controls the opening and closing of the oil passage so that the oil jet does not inject the oil into the piston in the non-injection area including the top dead center of the piston.

  In the lubricating device for an internal combustion engine configured as described above, the control unit opens and closes the oil passage by utilizing the magnetic action with the permanent magnet according to the distance from the permanent magnet that moves according to the phase of the piston. The opening / closing of the oil passage can be controlled according to the operation of the piston. That is, it is possible to control the opening and closing of the oil passage of the oil jet with a simple configuration without requiring complicated calculation using the ECU. Further, since the control unit controls the oil passage so that the oil jet does not inject oil into the piston in the non-injection region including the top dead center of the piston, the work amount of the oil jet in the non-injection region can be reduced. As a result, the fuel efficiency of the internal combustion engine can be improved. Since the distance from the oil jet to the piston is long in the non-injection region including the top dead center, even if the oil is ejected from the oil jet, the oil may not reach the desired portion of the piston. Therefore, even if the oil injection is stopped in the region including the top dead center, the cooling capacity of the piston is not reduced. On the other hand, since the distance between the oil jet and the piston is short in the injection region including the bottom dead center, the oil can reach the desired portion of the piston. As a result, the piston can be cooled reliably.

  Preferably, the permanent magnet is provided on the piston or crankshaft. In this case, since the piston or crankshaft has a large volume, it is easy to attach the permanent magnet. When a permanent magnet is provided on the piston, the phase of the piston can be directly reflected on the permanent magnet. When the permanent magnet is provided on the crankshaft, the temperature of the permanent magnet can be kept lower than when the piston is provided with the permanent magnet.

  Preferably, the piston is provided with a cooling channel, and the oil jet injects oil toward the cooling channel. In this case, since oil can be injected into the cooling channel, the piston can be cooled efficiently.

  According to the present invention, it is possible to control the oil jet with a simple structure and reduce the work of the oil pump that supplies oil to the oil jet to improve fuel consumption. Can be provided.

FIG. 3 is a schematic diagram of a lubricating device for an internal combustion engine according to the first embodiment. FIG. 3 is a schematic diagram of a lubricating device for an internal combustion engine according to the first embodiment. It is a graph which shows the relationship between the opening and closing of an electromagnetic on-off valve, and the phase of a piston. FIG. 6 is a schematic diagram of a lubricating device for an internal combustion engine according to a second embodiment. FIG. 6 is a schematic diagram of a lubricating device for an internal combustion engine according to a second embodiment. FIG. 9 is a schematic diagram of a lubricating device for an internal combustion engine according to a third embodiment. FIG. 9 is a schematic diagram of a lubricating device for an internal combustion engine according to a fourth embodiment. FIG. 9 is a schematic diagram of a lubricating device for an internal combustion engine according to a fifth embodiment. FIG. 9 is a schematic diagram of a lubricating device for an internal combustion engine according to a fifth embodiment.

  Hereinafter, an internal combustion engine according to each embodiment of the present invention will be described with reference to the drawings. In the following description, the same or corresponding parts in the drawings will be designated by the same reference numerals and the description thereof will not be repeated.

(Embodiment 1)
(overall structure)
1 and 2 are schematic diagrams of a lubricating device for an internal combustion engine according to the first embodiment. Note that FIG. 1 shows a case where the distance between the permanent magnet and the electromagnetic on-off valve is short, and FIG. 2 shows a case where the distance between the permanent magnet and the electromagnetic on-off valve is long.

  As shown in FIG. 1, the lubricating device for the internal combustion engine 1 includes a piston 10 that is connected to a connecting rod 19 and reciprocates, and oil 26 is supplied from an oil pump 70 to supply the oil 26 to the piston 10 from the connecting rod 19 side. Control for controlling the oil jet from the oil jet by the magnetic action of the oil jet 20 to be jetted, the permanent magnet 13 that moves according to the phase of the piston 10, and the permanent magnet 13 according to the distance from the permanent magnet 13. The electromagnetic on-off valve 21 as a part is provided. Electromagnetic opening / closing to prevent the oil jet 20 from injecting oil into the piston 10 in the injection region including the bottom dead center of the piston 10 and preventing the oil jet 20 from injecting oil into the piston 10 in the non-injection region including the top dead center of the piston 10. The valve 21 controls the oil injection from the oil jet 20.

  A cooling channel 11 is provided in the piston 10. The cooling channel 11 is a hollow portion provided in the piston 10. The oil cools the wall surface of the cooling channel 11 by injecting the oil 26 into the cooling channel 11. Thereby, the piston 10 can be cooled. The cooling channel 11 does not necessarily have to be provided.

  A permanent magnet 13 is provided at the lower end of the skirt 10a of the piston 10. Although the permanent magnet 13 is provided only on one skirt 10a in this embodiment, it may be provided on the skirt 10b on the opposite side.

  The connecting rod 19 connects the piston 10 and the crankshaft 17. A piston pin 10p is attached to the small end of the connecting rod 19. A counterweight 18 is provided on the crankshaft 17.

  The oil jet 20 is provided at a position apart from the piston 10. The oil jet 20 is fixed to, for example, a cylinder block. The oil jet 20 has a nozzle 20a.

  The electromagnetic opening / closing valve 21 is connected to the oil jet 20. The electromagnetic on-off valve 21 controls injection of the oil 26 from the oil jet 20. The electromagnetic opening / closing valve 21 is connected to the oil passage 29. The oil passage 29 is connected to the oil pump 70. Oil 26 is supplied from the oil passage 29 to the electromagnetic opening / closing valve 21. The oil pump 70 may be an electric type that is driven by a motor or a mechanical type that is driven by utilizing the rotation of a crankshaft.

  A power supply 22 for opening and closing the electromagnetic on-off valve 21 is connected to the electromagnetic on-off valve 21 by a power supply line 22a. The power supply 22 is composed of, for example, a battery mounted on the vehicle.

  The electromagnetic on-off valve 21 is provided with a sensor 21b for detecting the magnetic force of the permanent magnet 13. When the magnetic force of the permanent magnet 13 detected by the sensor 21b is equal to or larger than a predetermined value, the electromagnetic opening / closing valve 21 opens. As a result, the oil 26 is ejected from the nozzle 20a. When the magnetic force of the permanent magnet 13 detected by the sensor 21b is less than the predetermined value, the electromagnetic opening / closing valve 21 is closed. As a result, the oil 26 is not jetted from the nozzle 20a.

  The magnetic force of the permanent magnet 13 detected by the sensor 21b is related to the distance between the sensor 21b provided in the electromagnetic opening / closing valve 21 and the permanent magnet 13. When the distance between the sensor 21b and the permanent magnet 13 is long, the magnetic force of the permanent magnet 13 detected by the sensor 21b becomes weak. When the distance between the sensor 21b and the permanent magnet 13 is short, the magnetic force of the permanent magnet 13 detected by the sensor 21b becomes strong.

(motion)
In FIG. 1, the piston 10 is located at the bottom dead center. The distance between the permanent magnet 13 and the sensor 21b is L1, and the permanent magnet 13 is close to the sensor 21b. Therefore, the magnetic force of the permanent magnet 13 detected by the sensor 21b is strong. The electromagnetic on-off valve 21 opens because the sensor 21b detects a strong magnetic force. The oil 26 is sprayed as the spray 25 from the nozzle 20a. Since the diameter of the spray is smaller than the diameter of the inlet 12 of the cooling channel 11, the oil 26 is introduced into the cooling channel 11. Thereby, the piston 10 can be cooled.

  In FIG. 2, the piston 10 is located at the top dead center. The distance between the permanent magnet 13 and the sensor 21b is L2 (> L1), and the permanent magnet 13 is separated from the sensor 21b. Therefore, the magnetic force of the permanent magnet 13 detected by the sensor 21b is weak. Since the sensor 21b detects a weak magnetic force, the electromagnetic opening / closing valve 21 is closed. The oil 26 is not jetted from the nozzle 20a. If the oil 26 is injected, the spray of the oil 26 spreads in the area indicated by the dotted line 25a. Since the diameter D2 of the spray is larger than the diameter D1 of the inlet 12, even if the oil 26 is injected, some oil 26 does not enter the inlet 12.

  FIG. 3 is a graph showing the relationship between the opening / closing of the solenoid valve and the phase of the piston. The position of the permanent magnet 13 from the upper surface of the bore changes with the crank angle (phase of the piston 10) as shown by the curve 503. The distance is greatest at bottom dead center (BDC), and the distance is smallest at top dead center (TDC). The distance between the sensor 21b and the permanent magnet 13 also changes similarly to the curve 503 of FIG. 3, and is the minimum at the bottom dead center and the maximum at the top dead center. A straight line 501 shows the opening / closing position of the electromagnetic on-off valve 21, and a straight line 502 shows the injection timing at which the diameter D2 of the spray becomes larger than the diameter D1 of the inlet 12 of the cooling channel 11. When spraying at a crank angle closer to the top dead center than the straight line 502, the diameter D2 of the spray becomes larger than the diameter D1 of the inlet 12.

  In this embodiment, the injection region including the bottom dead center is provided on the bottom dead center side of the straight line 502. The area other than the injection area is the non-injection area including the top dead center. Injection regions and non-injection regions are present alternately according to the phase of the piston (crank angle).

  If it is important to put the spray 25 into the cooling channel 11 via the inlet 12, it is necessary to inject the oil 26 closer to the bottom dead center than the straight line 502. On the other hand, if it is not necessary to put the spray 25 into the inlet 12, the oil 26 may be injected at the top dead center side of the straight line 502.

(Action, effect)
In the above lubricating apparatus for the internal combustion engine 1, the electromagnetic opening / closing valve 21 is operated by the magnetic action of the permanent magnet 13 and the sensor 21b at a crank angle near the bottom dead center of the piston 10 without inputting a control signal from the outside. Can be opened and closed. As a result, the solenoid 26 can be opened and closed to inject the oil 26 without using the ECU. As a result, it is possible to control the oil jet 20 with a simple configuration.

  Since the diameter D2 of the spray of the oil 26 is smaller than the diameter D1 of the inlet 12 of the cooling channel 11 to inject the oil 26, the ratio of the injected oil 26 flowing into the cooling channel 11 can be increased.

  In the non-injection region including the vicinity of the top dead center, the distance between the oil jet 20 and the piston 10 becomes large, and the oil 26 jetted from the oil jet 20 hardly enters the cooling channel 11. At this timing, the work of the oil pump 70 can be reduced by stopping the injection of the oil 26. As a result, the fuel efficiency of the internal combustion engine 1 can be improved.

  In the non-injection region including the top dead center, as described above, it is difficult for oil to enter the cooling channel 11. Therefore, even if the oil injection is stopped in this portion, the cooling capacity of the piston 10 is not reduced. As a result, by adopting the above configuration, the fuel consumption of the internal combustion engine 1 can be improved without lowering the cooling capacity of the piston 10.

(Embodiment 2)
4 and 5 are schematic diagrams of a lubricating device for an internal combustion engine according to the second embodiment. As shown in these figures, the lubricating device for the internal combustion engine 1 according to the second embodiment is different from the lubricating device for the internal combustion engine 1 according to the first embodiment in that the flow of the oil 26 is controlled by the spring 31 and the valve 32. different.

  The valve 32 is an iron ball. The valve 32 is pushed by the spring 31 and is attracted by the permanent magnet 13. The distance between the permanent magnet 13 and the valve 32 determines the force with which the permanent magnet 13 attracts the valve 32.

  As shown in FIG. 4, when the distance between the permanent magnet 13 and the valve 32 is large at L2, the force with which the permanent magnet 13 attracts the valve 32 is small. Therefore, the valve 32 is pushed by the spring 31 and the valve 32 closes the oil passage 29. As a result, the oil 26 is not supplied to the oil jet 20, and the oil 26 is not ejected from the nozzle 20a.

  As shown in FIG. 5, when the distance between the permanent magnet 13 and the valve 32 is small at L1, the force with which the permanent magnet 13 attracts the valve 32 is large. Therefore, the valve 32 compresses the spring 31 and the valve 32 opens the oil passage 29. As a result, the oil 26 is supplied to the oil jet 20, and the oil 26 is jetted from the nozzle 20a.

  In the lubricating device for the internal combustion engine 1 according to the second embodiment configured as described above, the injection of the oil 26 can be controlled by the spring 31 and the valve 32 as the control unit. Therefore, it is not necessary to use the power supply 22 as in the first embodiment, so that power consumption can be reduced. Further, since it is not necessary to provide the electromagnetic opening / closing valve 21, the sensor 21b, the power source 22, and the power source line 22a for each cylinder, it is not necessary to provide a conductive portion in an oil atmosphere. As a result, reliability is improved.

(Embodiment 3)
FIG. 6 is a schematic diagram of a lubricating device for an internal combustion engine according to the third embodiment. The lubricating device for the internal combustion engine 1 according to the third embodiment is different from the electromagnetic opening / closing valve 21 in that the flow control valve 27 and the oil passage 28 for supplying the oil 26 to the flow control valve 27 are provided. Of the internal combustion engine 1 according to the first embodiment.

  The oil 26 that has passed through the flow rate adjusting valve 27 is supplied to the oil jet 20 and is ejected from the nozzle 20a. The oil passage 28 is provided in parallel with the oil passage 29.

  The electromagnetic on-off valve 21 opens and closes at the same timing as in the first embodiment. The flow rate adjusting valve 27 is opened under the condition that it is better to increase the heat input amount from the piston 10 to the oil 26 during warm-up operation or high-speed / high-load operation, and the oil 26 is injected into the piston 10. A large amount of oil 26 is injected into the piston 10 by opening the flow rate adjusting valve 27 during warm-up operation. Therefore, the heat transfer from the piston 10 to the oil 26 is promoted, and the oil temperature rises early. As the oil temperature rises, the oil viscosity decreases, and the friction of the sliding portion can be reduced. During high rotation and high load, a large amount of oil 26 is injected into the piston by opening the flow rate adjusting valve 27. Therefore, the transfer of heat from the piston 10 to the oil 26 is promoted, and the piston can be sufficiently cooled. As a result, it is possible to suppress a decrease in strength of the piston due to insufficient cooling of the piston.

(Embodiment 4)
FIG. 7 is a schematic diagram of a lubricating device for an internal combustion engine according to the fourth embodiment. The lubricating device for internal combustion engine 1 according to the fourth embodiment is different from the lubricating device for internal combustion engine 1 according to the first embodiment in that two nozzles 20a and 20b are provided.

  Nozzle 20a injects oil 26 at the same timing as nozzle 20a according to the first embodiment.

  The nozzle 20b injects the oil 26 toward the piston 10 at a timing different from that of the nozzle 20b. The nozzle 20b may inject the oil 26 into the piston 10 when the nozzle 20a does not inject the oil 26. The nozzle 20b may inject the oil 26 at the same timing as the timing at which the nozzle 20a injects the oil 26.

  The lubricating device for the internal combustion engine 1 configured as described above also has the same effect as the lubricating device for the internal combustion engine 1 according to the first embodiment.

(Embodiment 5)
8 and 9 are schematic diagrams of a lubricating device for an internal combustion engine according to the fifth embodiment. In Embodiments 1 to 4, the piston 10 is provided with the permanent magnet 13, whereas in Embodiment 5, the counterweight 18, which is a part of the crankshaft 17, is provided with the permanent magnet. Different from the lubricating device for the internal combustion engine 1 according to the first embodiment.

  As shown in FIG. 8, when the piston 10 is located at the bottom dead center, the counterweight 18 approaches the piston 10. In this state, the distance L1 between the permanent magnet 13 provided on the counterweight 18 and the sensor 21b is short. Therefore, the magnetic force of the permanent magnet 13 detected by the sensor 21b is strong. The electromagnetic on-off valve 21 opens because the sensor 21b detects a strong magnetic force. The oil 26 is sprayed as the spray 25 from the nozzle 20a. Since the diameter of the spray is smaller than the diameter of the inlet 12 of the cooling channel 11, the oil 26 is introduced into the cooling channel 11. Thereby, the piston 10 can be cooled.

  As shown in FIG. 9, the counterweight 18 moves away from the piston 10 when the piston 10 is located at the top dead center. In this state, the distance L2 between the permanent magnet 13 provided on the counterweight 18 and the sensor 21b is long. Therefore, the magnetic force of the permanent magnet 13 detected by the sensor 21b is weak. Since the sensor 21b detects a weak magnetic force, the electromagnetic opening / closing valve 21 is closed. The oil 26 is not jetted from the nozzle 20a.

  The lubricating device for an internal combustion engine 1 according to the fifth embodiment thus configured has the same effects as the lubricating device for the internal combustion engine 1 according to the first embodiment. Further, since the counterweight 18 has a lower temperature than the piston 10, the possibility that the magnetic characteristics of the permanent magnet 13 are deteriorated by heat is reduced.

  The above disclosure is illustrative in all respects and not restrictive. The technical scope of the present invention is shown by the claims, and is intended to include meanings equivalent to the claims and all modifications within the scope.

  The present invention can be used in, for example, a lubricating device for an internal combustion engine having an oil jet for injecting oil into a piston.

  1 Internal Combustion Engine, 10 Pistons, 10a, 10b Skirt, 10p Piston Pin, 11 Cooling Channel, 12 Inlet, 13 Permanent Magnet, 17 Crank Shaft, 18 Counter Weight, 19 Connecting Rod, 20 Oil Jet, 20a, 20b Nozzle, 21 Electromagnetic on-off valve, 21b sensor, 22 power supply, 22a power supply line, 25 spray, 26 oil, 27 flow rate adjusting valve, 28, 29 oil passage, 31 spring.

Claims (3)

A piston connected to a connecting rod and reciprocating,
An oil jet that is supplied with oil from an oil pump and injects oil from the connecting rod side to the piston,
A permanent magnet that moves according to the phase of the piston,
A control unit that controls the injection of oil from the oil jet by a magnetic action with the permanent magnet according to the distance from the permanent magnet,
The control is performed such that the oil jet injects oil into the piston in an injection area including the bottom dead center of the piston and does not inject the oil into the piston in a non-injection area including top dead center of the piston. The part is a lubrication device for an internal combustion engine that controls oil injection from an oil jet.   The lubricating device for an internal combustion engine according to claim 1, wherein the permanent magnet is provided on the piston or the crankshaft.   The lubricating device for an internal combustion engine according to claim 1, wherein a cooling channel is provided in the piston, and the oil jet injects oil toward the cooling channel.