JP2021032173A - Lubrication device for engine - Google Patents

Abstract

To reduce a mechanism for distribution to enable an amount of lubricant supplied to each unit to be adjusted, upon supplying lubricant to each unit of an engine.SOLUTION: A lubrication device of an engine has a multi-way valve 22 with three or more directions downstream of an oil pump 13, wherein downstream flow paths 23a, 23b connected to the multi-way valve 22 have different lengths up to a confluent point 24, and has a branch point Q1 where a flow path for a cylinder block 30 branches downstream of the confluent point 24. The lubrication device is used to adjust an amount of oil by switching the multi-way valve 22.SELECTED DRAWING: Figure 1

Description

The present invention relates to the distribution of lubricating oil used in automobile engines and the like.

The engine lubrication mechanism generally has a structure in which the lubricating oil introduced into the cylinder head above the engine passes through an oil drop hole provided in the cylinder block and falls into an oil pan provided below the engine. There is. An oil screen is provided near the center of the oil pan, and the oil pump sucks up the lubricating oil and introduces it into the cylinder head. Lubricating oil is circulated by repeating this.

In addition, the lubricating oil needs to be supplied in a sufficient amount to the cylinder block having the crank journal and the crank pin. Therefore, not only the lubricating oil is introduced into the cylinder head and indirectly supplied to the cylinder block, but also a path for introducing the lubricating oil directly into the cylinder block may be provided.

However, the lubricating oil also has a cooling effect. On the other hand, Patent Document 1 describes an oil amount adjusting device that limits the amount of refueling when the engine is to be heated and promotes the temperature rise by frictional heat. In this oil amount adjusting device, the amount of oil supplied to the engine is collectively adjusted by the relief valve, but it is premised that the oil flow rate cannot be reduced locally. Switching between a valve open state that passes through a large flow path with a large path cross-sectional area and a valve closed state that passes through a small flow path with a smaller path cross-sectional area than the large flow path, intervening between the crankshaft and multiple bearings. It is described that the flow rate of the oil supplied to all the sliding parts is switched according to the temperature.

In addition, the amount of lubricating oil consumed differs depending on the site. On the other hand, there is a method of preparing a separate lubricating oil pump so that the lubricating oil is not wasted, but the device becomes complicated. Therefore, by controlling a three-way valve that switches between the state where the lubricating oil pump is connected to the journal bearing and the state where the lubricating oil pump is connected to the lubricating oil tank via the return passage, lubrication is performed from the lubrication path to each lubricated part. Patent Document 2 describes a lubricating oil supply device capable of adjusting the amount of return to the oil tank and individually distributing the amount of lubricating oil supplied to each lubricated portion by one lubricating oil pump at a predetermined ratio.

Further, Patent Document 3 describes that the oil is branched from the main gallery (main flow path) to which the oil is supplied from the oil pump, and the oil is flowed through the oil passage that can receive the heat of the exhaust port to raise the temperature. Each branched route is called a bypass passage, but each route is a supply route to a separate part in the engine, and the routes do not overlap. A valve that can be opened and closed individually is attached to each path to adjust the supply amount to each part.

Japanese Unexamined Patent Publication No. 2015-4299 Japanese Unexamined Patent Publication No. 7-224628 Japanese Unexamined Patent Publication No. 2012-137016

However, providing valves in individual paths or using separate pumps to regulate the supply to each part of the engine complicates the equipment. However, without the provision of individual valves and pumps, the oil distribution ratio at each branch point remained fixed and could not be adjusted.

On the other hand, if a sufficient amount of lubricating oil is to be supplied to various places so as not to be insufficient, the required lubricating oil pressure will be excessively applied, and the oil pump work will increase. In addition, the amount of leakage at each point where the lubricating oil is discharged also increases. For this reason, the engine friction loss has also become excessive. Further, since the cooling with the lubricating oil is excessively performed, the completion time from the start of the cold engine to the warm-up is also excessive.

Therefore, an object of the present invention is to make it possible to adjust the discharge amount from a plurality of oil discharge ports without relying on valves or pumps for individual paths.

This invention
A lubricant that supplies lubricating oil to the engine.
The main flow path provided downstream of the oil pump and
A multi-way valve provided in the main flow path and branching into three or more directions,
The first lubricating oil group piping that branches from the main flow path at _{the branch point (Q 1} ) located downstream of the multi-sided valve,
The branches and the main flow path at a multi-way valve, and a bypass passage that connects the junction to merge with the branch point (Q ₁₎ the main flow path from upstream,
The above problem is solved by a lubrication device characterized in that the lengths of the main flow path portion section from the multi-sided valve to the confluence and the bypass flow path of the main flow path are different.

The flow rate of lubricating oil in the flow path beyond the oil pump is characterized by decreasing according to the distance from the oil pump. The present invention utilizes this to provide the bypass flow path that branches from the main flow path at the multi-way valve and joins at the confluence, and is a partial section of the main flow path from the multi-way valve to the confluence of the main flow path. By changing the length of the bypass flow path and the bypass flow path, the flow rate of the lubricating oil in the downstream can be switched by switching between the case of passing through the main flow path portion section and the case of passing through the bypass flow path. I made it.

Further, the bypass flow path is formed longer than the distance from the multi-sided valve of the main flow path to the confluence point, and the lubricating oil flows through the bypass flow path from engine start to warm-up. A configuration having a control means for controlling the multi-way valve can be adopted. The distance from the multi-way valve of the main flow path to the confluence point is, that is, the main flow path partial section parallel to the bypass flow path. From engine start to warm-up, the flow rate of the lubricating oil is reduced by allowing the lubricating oil to flow through the bypass flow path, which is longer than the main flow path portion section, and the cooling effect of the lubricating oil is temporarily suspended. It can be reduced and warmed up quickly.

Further, between the joining point and the branch point (Q _1), provided with a throttle valve, the control means may adopt a configuration for adjusting the amount of lubricant supplied by opening and closing the throttle valve .. Normally, the throttle valve is controlled in a throttled state, and in an emergency when a predetermined condition is satisfied, the throttle valve is controlled to be opened. For example, such as when the temperature of the branch point (Q ₁₎ is or exceeds the prescribed value, the oil amount or has decreased beyond a predetermined value, receives a signal indicating the possibility of seizure is occurring ..

Furthermore, the first lubricating oil group piping is provided with a second lubricating oil group piping branching from the main flow path at a branching point (Q _{2 ) located downstream from the branch point (Q 1} ) to the first lubricating oil group piping. The oil group piping can supply lubricating oil to the cylinder block, and the second lubricating oil group piping can adopt a configuration in which lubricating oil is supplied to the cylinder head. Cylinder blocks specifically include cranks that tend to require a large amount of lubricating oil. The first lubricating oil group pipe supplies lubricating oil to the cylinder block, and the second lubricating oil group pipe supplies lubricating oil to the cylinder head. The first lubricating oil group pipes for split from the main flow path at a branch point located upstream (Q _1), it is possible to secure a large amount of flow. Further, in the present invention, the lubricating oil is allowed to pass through the bypass flow path, which is relatively longer than the main flow path portion section until warming up, so that the supply amount of the lubricating oil to the cylinder block is not seized. The temperature rise is promoted by suppressing the cooling effect of the lubricating oil. By allowing the lubricating oil to pass through the relatively short main flow path portion section after warming up, the pressure at _{the branch point (Q 1) of the first lubricating oil group piping is improved, and the branch point (Q 1) is improved.} Increase the amount of lubricating oil supplied to the cylinder block by dividing it in _1). When the supply amount of the lubricating oil supplied to the cylinder block increases, the supply amount of the lubricating oil to the cylinder head supplied by the second lubricating oil group piping decreases accordingly. That is, when it is desired to increase the amount of lubricating oil supplied to the first lubricating oil group piping that supplies the cylinder block, the multi-way valve is controlled so as to pass through the main flow path portion section having a short length to the branch point. and, wherein when it is desired to increase the first lubricating oil group ratio of feed to the second lubricating oil group pipe supply amount to reduce the ratio of the that downstream of the site on the pipe, the branch point (Q ₁₎ By controlling the multi-way valve so that it passes through a bypass flow path having a long length up to, the amount of lubricating oil supplied can be adjusted by one multi-way valve.

According to the present invention, the lubricating oil supplied to each part by adjusting the multi-way valve provided upstream without providing a separate valve or a separate pump at each part of the engine branching from the main flow path. The amount of can be adjusted.

Functional block diagram showing an example of an embodiment of the lubrication device according to the present invention. The figure which shows the transition of the pressure when the throttle valve is throttled and passes through a bypass flow path. The figure which shows the transition of the pressure when the throttle valve is throttled and passes through the main flow path part section. The figure which shows the transition of the pressure when the throttle valve is opened and passes through a bypass flow path. The figure which shows the transition of the pressure when the throttle valve is opened and passes through the main flow path partial section. The flow chart which shows the operation procedure example of the lubrication apparatus which concerns on this invention.

Hereinafter, the present invention will be described in detail. The present invention is a lubricating device that mainly introduces lubricating oil to be introduced into an engine mounted on a vehicle into an engine and circulates the lubricating oil.

A functional block diagram of an embodiment of a lubrication device according to the present invention is shown in FIG. The lubricating oil accumulated in the oil pan 11 is sucked up by the oil pump 13 via the oil screen 12. Lubricating oil is discharged from the discharge port of the oil pump 13 by applying pressure to the pipe 16 constituting the main flow path 21. The pipe 16 constituting the main flow path 21 is provided with a relief valve 14 for releasing pressure when the pipe is closed or the valve provided downstream is closed. The tip of the relief valve 14 is arranged so as to return to the oil pan 11.

Further, the pipe 16 may be provided with a branch to the balancer unit 15 that suppresses the vibration of the engine, in addition to the relief valve 14. For convenience of piping, it is preferable to provide it immediately after the relief valve 14. By providing a branch to the balancer unit 15 before the multi-way valve 22, which will be described later, the amount of lubricating oil supplied to the balancer unit 15 can be stabilized regardless of the switching of the multi-way valve 22. The balancer unit 15 may be included in the group of parts supplied by the first lubricating oil group pipe 31, which will be described later, or may be included in the group of parts supplied by the second lubricating oil group pipe 42. It may be included in the group of other parts.

Further, although not shown, an embodiment in which an oil filter is provided downstream of the oil pump 13 may be used. However, the oil filter dampens the pressure of the lubricating oil sent to the subsequent parts. Therefore, when the pressure of the lubricating oil is appropriately adjusted by the lubricating device according to the present invention, the structure and arrangement of the oil filter are set so as not to hinder the switching of the distribution rate of the lubricating oil by the lubricating device according to the present invention. It is preferable to do so.

At the end of the main flow path 21, lubricating oil for the first lubricating oil group piping 31 that supplies lubricating oil to the cylinder block 30 including the crankshaft and the piping group including the second lubricating oil group piping 42 downstream of the first lubricating oil group piping 31. branch point Q ₁ is provided for branching and. Upstream from the branch point Q ₁ is the piping 16 of the main flow passage 21, the multiposition valve 22 is provided. A three-way valve is described as the multi-way valve 22 in the embodiment shown in FIG. However, the present invention is not limited to the three-way valve, and a four-way or more multi-way valve may be used.

The piping is branched at the multi-way valve 22, and the lubricating oil supplied from the oil pump 13 is sent to different paths by switching the multi-way valve 22. The respective routes meet at the downstream confluence 24. However, each path from the multi-sided valve 22 to the confluence 24 has channels having different lengths from each other. In this embodiment, the flow path having the shortest length from the multi-way valve 22 to the confluence point 24 is called a main flow path portion section 23b, and is a detour that is parallel to the main flow path portion section 23b and longer than the main flow path portion section. Is called a bypass flow path 23a. The length of the flow path from the oil pump 13 to the confluence point 24 is short when passing through the main flow path portion section 23b and becomes long when passing through the bypass flow path 23a. Such switching of the length of the flow path can be performed by switching the valve of the multi-sided valve 22. When the multi-way valve 22 is a valve having four or more sides, it is connected to the third and fourth flow paths having different lengths up to the confluence point 24 from both the main flow path portion section 23b and the bypass flow path 23a. You may leave it as it is.

Although not shown, it is possible to select a configuration in which the bypass flow path 23a is shorter than the main flow path portion section 23b constituting the main flow path 21. In that case, the multi-way valve 22 is controlled so as to pass through the bypass flow path 23a when the flow path is to be shortened.

The control of the multi-way valve 22 is performed by the control means executed by the control device 27. The control device 27 may be a dedicated device. Further, the engine control unit used by the vehicle equipped with the lubrication device according to the present invention may also function as the control device 27.

The main flow passage 21 is a downstream of the merging point 24, upstream of the branch point Q _1, to have a throttle valve 25 preferably. The control means of the control device 27 opens and closes the throttle valve 25 to increase or decrease the cross-sectional area of the flow path and increase or decrease the amount of lubricating oil supplied accordingly. That is, when the throttle valve 25 is throttled, the pressure and flow rate of the lubricating oil downstream thereof can be reduced. On the other hand, when the throttle valve 25 is opened, the lubricating oil can be fed downstream without reducing the pressure and flow rate of the lubricating oil. The control means of the control device 27 can be controlled so that the throttle valve 25 is normally throttled and the throttle valve 25 is opened in an emergency. Emergency and is, for example increased above the specified range of temperature at the branch point Q _1, loss of more than a defined range of oil quantity in the downstream, and the like when detecting seizure. In both cases, the lubricating oil to be supplied is temporarily increased rapidly to improve the lubricating performance and the cooling effect.

The control means of the control device 27 may also control the throttle valve 25. That is, the control means may be able to collectively control the throttle valve 25 in cooperation with the control of the multi-sided valve 22.

Branch point Q ₁ represents a first lubricating oil group pipe 31 for supplying lubricating oil to the cylinder block 30 including the crank journal 32 and crankpin 33, pipe for supplying lubricating oil to the rest of the site to be supplied with lubricating oil 41 It is a branch point that branches to and. This is the remaining sites include a cylinder head 40, and supplies the lubricating oil in the second lubricating oil group pipe 42 which branches in the preceding branch point Q ₂ of the pipe 41 to the cylinder head 40.

The cylinder block 30 to which the first lubricating oil group pipe 31 supplies the lubricating oil may include a crank, and does not have to be all parts related to the crank. The part where it is desirable for the first lubricating oil group pipe 31 to supply the lubricating oil can be appropriately selected and set as a part which is desired to be warmed quickly especially at the time of starting in a cold state and a part where the amount of oil is to be significantly changed. However, it is preferable that the first lubricating oil group pipe 31 collectively supplies the portion that requires a particularly large amount of oil.

Is branched at the branch point Q _1, the lubricating oil supplied to the first lubricating oil group pipe 31 is in this embodiment supplied to the crank journal 32 that is included in the cylinder block 30. A part of it is supplied to the crank pin 33 and then falls into the oil pan 11, and the rest is dropped into the oil pan 11 as it is.

On the other hand, the tip of the pipe 41 is appropriately branched. In this embodiment, are branched at the branch point Q _2, the second lubricating oil group pipe 42 toward the upper portion of the cylinder head 40, the pipe 43 toward the lower side of the balancer gear housing 69, the pipe 44 toward the timing chain tensioner 66 Divided into. The downstream a and further provided another branch point Q ₃ on the upstream of the branch point Q ₂ of the branch point Q _1, and branches the sub branch pipe 51.

Examples of the portion included in the cylinder head 40 include a roller rocker arm 61, a cam journal 62, a cam oil shower 63, and the like. Lubricating oil is further branched from the second lubricating oil group pipe 42 and sent to each portion, and the sent lubricating oil finally falls into the oil pan 11.

The lubricating oil sent from the pipe 44 to the timing chain tensioner 66 falls to the oil pan 11 via the turbocharger 67.

The previous sub branch pipe 51, the timing chain jets 52, such as oil jet 53, the oil consumption assign relatively large portion of the branch point Q ₂ and subsequent sections. The introduced lubricating oil finally falls into the oil pan 11.

Lubricating apparatus according to the present invention, by switching the multi-way valve 22, the pressure of the lubricating oil at the branch point Q _1, it from a different pressure of the lubricating oil at the branch point Q ₂ to which is downstream can be adjusted one place .. The pressure of the lubricating oil is attenuated mainly by friction according to the length of the flow path from the discharge port 13a of the oil pump 13. Using this property, by switching the distance L from the discharge port 13a to the branch point Q _1, the attenuation width increased or decreased, can increase or decrease the pressure of the lubricating oil at the branch point Q _1. When the pressure at the branch point Q ₁ is increased, the amount of lubricating oil is increased to be supplied to the first lubricating oil group pipe 31. That is, by switching from the arrangement of the multi-way valve 22 passing through the bypass flow path 23a having a long flow path to the arrangement of the multi-way valve 22 passing through the main flow path portion section 23b having a short flow path, the first lubricating oil group piping 31 The proportion of lubricating oil supplied to the vehicle can be increased. On the contrary, when it is desired to temporarily reduce the ratio of the lubricating oil supplied to the first lubricating oil group pipe 31, the multi-way valve 22 is switched so as to pass through the bypass flow path 23a having a long flow path.

The relationship between the pressure of the lubricating oil in the valve branch point Q ₁ and the branch point Q ₂ Prefecture, will be described with reference to FIGS. 2 and 3 show a pressure change in a state where the throttle valve 25 is throttled and the pressure downstream of the throttle valve 25 is reduced. 4 and 5 show the pressure change in the state where the throttle valve 25 is open. Of these, FIGS. 2 and 3 will be described. FIG. 2 shows a state in which the multi-way valve 22 is set so that the flow path (L _{2 ) up to the branch point Q 1 is connected to the long bypass flow path 23a.} FIG. 3 shows a state in which the multi-way valve 22 is set so that the flow path (L _{1 ) to the branch point Q 1 is connected to the short main flow path portion section 23b.} The oil tank on the left in the figure is a virtual one representing the oil pressure generated by the oil pump 13. The pressure of the discharge port 13a of the oil pump 13 is represented as _{a virtual height H 0 from the discharge port 13a to the liquid level.} The flow rate Q at the discharge port 13a is the product of the cross-sectional area A and the flow velocity v. From Torricelli's theorem, the law of equation (1) below holds. Note that g is the gravitational acceleration, and H ₀ is a virtual height (depth) from the liquid surface indicating the pressure at the discharge port 13a.

Q = A × v = A × (2 × g × H ₀ ) …… (1)

However, as for the pressure at each position of the main flow path 21, the pressure loss increases according to the distance from the discharge port 13a. Therefore, if the pressure at each location in the pipe is tentatively shown by the virtual height H, as shown by the solid line in the graph of FIG. 2, the virtual height H decreases as the distance from the discharge port 13a increases. It will be. Further, since the cross-sectional area A is narrowed by the throttle valve 25 provided in the middle, the virtual height H corresponding to the actual pressure is gradually attenuated as represented by the broken line further lowered from the solid line. .. The pressure at the branch point Q ₁ is composed attenuation due to loss in accordance with the distance L ₂ from the discharge port 13a, and corresponds to the virtual height H ₁ which decreases with the reduction by the throttle valve 25. Supply of lubricating oil is made from the branch point Q ₁ by this pressure to the first lubricating oil group pipe 31. After the branch point Q ₁ , the pressure is reduced by the amount of the pressure divided into the first lubricating oil group pipe 31 due to the branching, so that the virtual height H _1a indicating the pressure is greatly reduced from H _1. Thereafter, the distance from the further discharge opening 13a approaches the branch point Q ₂ becomes large, virtual height H also continue to decrease, the branch point Q ₂ in the virtual height H indicative of the pressure accordingly ₂ is even lower than _{H 1a.} Moreover, further branched at the branch point Q _2, the virtual height indicating the pressure remaining in the pipe 44 becomes H _2a decreases further. As described above, it decreases as _{H 1} > H _1a > H ₂ > H _2a. Actually, the towards the branch point Q ₂ of prior branch point Q _1, there is a case where the height of the pipe is raised. In this case, since the _{pressure at the branch point Q 2} is further lowered, the _{virtual heights H 2} and H ₂ a indicating the pressure around _{the branch point Q 2} are further lowered as compared with FIG.

By switching the multi-way valve 22, changing from the bypass flow passage 23a to be connected to the main passage part section 23b, it is shorter in length up to the branch point Q ₁ as shown in FIG. _{3 (L 2> L 1)} . Then, the damping width of the pressure up to the branch point Q ₁ is reduced. _{Therefore, the virtual height H 3} in the situation of FIG. 3 showing the pressure at the branch point Q ₁ is higher than the _{virtual height H 1} in the situation of FIG. 2 in which the multi-way valve 22 is connected to the bypass flow path 23a. It gets higher. Thus, the amount of oil supplied from the branch point Q ₁ to the first lubricating oil group pipe 31 can be increased than the status of FIG. Incidentally, the branch point Q ₁ after the pipe 41 and the second lubricating oil group pipe 42, the pressure in the pipe 44 and the like is entirely the followed higher tendency embodiment of Figure 2, similar to the situation in Figure 2, It gradually decreases before and after the branch point, and as the distance from the discharge port 13a increases, the virtual height H indicating the pressure also decreases. Therefore, H ₃ > H ₁ and H ₃ > H _3a > H ₄ > H _4a .

The situation of FIG. 2 and the situation of FIG. 3 can be changed only by switching the multi-way valve 22. Thus it is possible to control the amount of lubricating oil supplied from the branch point Q ₁ to the first lubricating oil group pipe 31. At the same time, despite holding the length of the flow path between the branch point Q ₁ and the branch point Q _2, to be adjusted by the lubricating oil flow rate is also multi-way valve 22 to be supplied to the branching point Q ₂ Become. Than the distance from the discharge port 13a to the branch point Q _1, instead it is a long distance to the branch point Q ₂ from the discharge port 13a, the rate of change which changes by switching the multiposition valve 22 is reduced. Due to this difference, even if the lubricating oil supplied to the first lubricating oil group pipe 31 is reduced by switching the multi-way valve 22, the amount of lubricating oil supplied to the second lubricating oil group pipe 42 is simply the same ratio. It does not decrease. Therefore, the branch point Q ₁ and the distance between the branch point Q _2, by properly setting the distance between each of the flow path from the multiposition valve 22 to the confluence 24, the multi-way valve 22 The amount of lubricating oil supplied to each part can be changed appropriately just by switching.

Next, a case where the throttle valve 25 is opened will be described. FIG. 4 shows a state in which the throttle valve 25 is open and the multi-sided valve 22 is connected to the bypass flow path 23a. FIG. 5 shows a state in which the throttle valve 25 is open and the multi-sided valve 22 is connected to the main flow path portion section 23b. Both because there is no decrease in pressure by the throttle valve 25, to the branch point Q ₁ is gradually decreased as shown by the solid line in only decrease virtual height indicating the pressure in accordance with the distance. Therefore, the virtual height H ₅ is the virtual height indicates the pressure at the branch point to Q ₁ in FIG. 2 that focus throttle valve 25 situation H indicative of the pressure at the branch point Q ₁ in the context of FIG. 4 Greater than _1. That is, H ₅ > H ₁ . Thus, the lubricating oil amount supplied from the branch point Q ₁ to the first lubricating oil group pipe 31 also increases from the status of FIG. Also, the virtual height H indicating the respective pressure branch point Q ₁ or later, both of which increased from the situation of FIG. 2. That is, H _5a > H _1a , H ₆ > H ₂ , and H _6a > H _2a .

Further, even in the state where the multi-way valve 22 is connected to the main flow path portion section 23b, there is no decrease in pressure due to the throttle valve 25 in the situation of FIG. 5 as compared with the situation of FIG. 3 in which the throttle valve 25 is throttled. Therefore, the amount of lubricating oil supplied by the branch point Q ₁ to the first lubricating oil group pipe 31 is much better in FIG. Further, the virtual height H indicating the pressure connected to the amount of lubricating oil supplied after that is also larger in the situation shown in FIG. 5 than in the situation shown in FIG. That is, H ₇ > H ₃ , H _7a > H _3a , H ₈ > H ₄ , and H _8a > H _4a .

The control device 27 that controls the lubrication device according to the present invention switches between the multi-sided valve 22 and the throttle valve 25 according to the temperature of each part and other conditions to realize efficient operation of the engine and ensuring safety. To do.

An operation example of the control means by the control device 27 that controls the lubrication device according to the present invention will be described with reference to FIG. It is assumed that the engine has not yet warmed up (S102) when the engine is started (S101). In this state, the control device 27 connects the multi-way valve 22 to the bypass flow path 23a, and the throttle valve 25 is throttled (S103). That is, the situation is adjusted to the situation shown in FIG. 2 above. In this setting, the minimum amount of oil that does not burn the cylinder block 30, the cylinder head 40, etc. flows through each of the first lubricating oil group pipe 31 and the second lubricating oil group pipe 42, and the lubricating oil flows. Cooling by the oil is suppressed and the temperature rise is promoted. Until the warm-up is completed (S104 → No), the state is continued. When the warm-up is completed (S104 → Yes), the control device 27 switches the multi-way valve 22 so as to be connected to the main flow path portion section 23b (S105). Normally, it is better to operate in this state.

During operation, if a situation is defined as an emergency, another control is performed. Emergency requirements include, for example, when the temperature of each part of the engine exceeds the preset allowable range, the amount of lubricating oil supplied to each part falls below the allowable range, or the possibility of seizure increases. is there. Specifically, the sensor detects that these situations have occurred, and switching is performed when the signal reaches the control device 27 (S106 → Yes). The throttle valve 25 is opened to rapidly increase the amount of lubricating oil supplied to each of the first lubricating oil group pipe 31 and the second lubricating oil group pipe 42 (S107). If the signal input from the sensor or the like does not meet the emergency requirements (S108 → Yes), the throttle valve 25 is throttled again to reduce the amount of lubricating oil (S109). After that, it will continue to operate until the requirements for an emergency are met.

Although not described in this flow, depending on the situation, the throttle valve 25 may be opened while the multi-way valve 22 is still connected to the bypass flow path 23a. Further, the connection destination of the multi-sided valve 22 may be switched between the main flow path portion section 23b and the bypass flow path 23a while the throttle valve 25 is left open.

11 Oil pan 12 Oil screen 13 Oil pump 13a Discharge port 14 Relief valve 15 Balancer unit 16 Piping 21 Main flow path 22 Multi-way valve 23a Bypass flow path 23b Main flow path Part section 24 Confluence point 25 Throttle valve 27 Control device 30 Cylinder block 31 First lubricating oil group piping 32 Crank journal 33 Crank pin 40 Cylinder head 42 Second lubricating oil group piping 41, 43, 44 Piping 51 Sub-branch piping 52 Timing chain jet 53 Oil jet 61 Roller rocker arm 62 Cam journal 63 Cam oil shower 66 Timing Chain Tensioner 67 Turbo Charger 69 Balancer Gear Housing Q ₁ , Q ₂ , Q ₃ Branch Point

Claims (4)

A lubricant that supplies lubricating oil to the engine.
The main flow path (21) provided downstream of the oil pump (13) and
A multi-way valve (22) provided in the main flow path (21) and branched into three or more directions.
The multi-way valve branch point located downstream of (22) (Q ₁₎ in the first lubricating oil group pipe branched from the main flow passage (21) (31),
The branched multi the main flow passage at-way valve (22) and (21), a bypass passage that connects the branch point (Q ₁₎ the main flow path from the upstream (21) merges with the merge point (24) With (23a)
Among the main flow paths (21), the lengths of the main flow path portion section (23b) from the multi-sided valve (22) to the confluence point (24) and the bypass flow path (23a) are different. Lubrication device. The bypass flow path (23a) is formed longer than the distance from the multi-sided valve (22) of the main flow path (21) to the confluence point (24).
The lubrication device according to claim 1, further comprising a control means for controlling the multi-sided valve (22) so that lubricating oil flows through the bypass flow path (23a) from engine start to warm-up. .. With throttle valve (25) between said merging point (24) and said branch point _{(Q 1),}
The lubrication device according to claim 2, wherein the control means adjusts the amount of lubricating oil supplied by opening and closing the throttle valve (25). A second lubricating oil group pipe (42) that branches from the main flow path (21) at a branch point (Q _{2 ) located downstream from the branch point (Q 1} ) of the first lubricating oil group pipe (31) is provided. ,
The first lubricating oil group pipe (31) supplies lubricating oil to the cylinder block (30).
The lubricating device according to any one of claims 1 to 3, wherein the second lubricating oil group pipe (42) supplies lubricating oil to the cylinder head (40).

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