WO2014103429A1 - 内燃機関のオイルジェット装置 - Google Patents
内燃機関のオイルジェット装置 Download PDFInfo
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- WO2014103429A1 WO2014103429A1 PCT/JP2013/072980 JP2013072980W WO2014103429A1 WO 2014103429 A1 WO2014103429 A1 WO 2014103429A1 JP 2013072980 W JP2013072980 W JP 2013072980W WO 2014103429 A1 WO2014103429 A1 WO 2014103429A1
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- WIPO (PCT)
- Prior art keywords
- oil
- valve
- oil jet
- valve housing
- port
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/06—Arrangements for cooling pistons
- F01P3/08—Cooling of piston exterior only, e.g. by jets
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
- F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/16—Pistons having cooling means
- F02F3/20—Pistons having cooling means the means being a fluid flowing through or along piston
- F02F3/22—Pistons having cooling means the means being a fluid flowing through or along piston the fluid being liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/02—Light metals
Definitions
- the present invention relates to an oil jet device for an internal combustion engine.
- the present invention relates to an improvement in a mechanism for switching between execution and stop of an oil jet.
- an engine internal combustion engine
- an oil supply system for supplying engine oil (lubricating oil) to a lubricated part or a cooled part. It has been.
- An oil jet device is connected to the oil supply system. A part of the engine oil discharged from the oil pump is supplied to the oil jet device and injected to the back side of the piston (hereinafter, this oil injection is referred to as an oil jet).
- the piston can be cooled by this oil jet, and for example, occurrence of knocking can be prevented.
- the oil jet device disclosed in the above publication is provided with a valve mechanism for adjusting the amount of the oil jet and switching between the execution and the stop of the oil jet.
- the valve mechanism is provided with a valve body that can move forward and backward toward an oil passage connected to the oil jet nozzle. A biasing force from a spring is applied to the valve body, and the opening area of the oil passage is changed by adjusting the position of the valve body by switching between excitation and non-excitation of the electromagnetic solenoid.
- valve mechanism having a valve body that changes the opening area of the oil passage
- a valve body that is movable in a direction substantially orthogonal to the extending direction of the oil passage is provided, and a valve that guides the movement of the valve body
- an opening communicating with the oil passage is formed on the side surface of the valve housing, and the opening and closing of the opening are switched by moving the valve body forward and backward within the valve housing.
- the valve body is moved forward inside the valve housing to close the opening and shut off the oil passage (valve closed state), and the valve body is moved backward.
- the valve housing is fixed to the oil passage by means such as press fitting or screw fastening.
- FIG. 7B is a cross-sectional view showing a closed valve state when a gap c is generated between the front end surface a1 of the valve housing a and the inner wall surface b1 of the oil passage b.
- the present invention provides an oil jet device for an internal combustion engine that can prevent oil leakage to the oil jet nozzle side in a closed state.
- the present invention is directed to an oil jet device of an internal combustion engine having an oil jet switching valve that opens and closes an oil passage communicating with an oil jet mechanism.
- the oil jet switching valve is inserted into an insertion hole extending in a direction substantially orthogonal to the extension direction of the oil passage and is movable along the extension direction of the insertion hole. It is the structure provided with the made valve housing. Further, in the oil jet device of the internal combustion engine, when the oil jet switching valve is closed, the tip of the valve housing is pressed toward the inner wall surface of the oil passage by receiving a biasing force from the biasing means. It has a configuration.
- the valve housing receives a biasing force from the biasing means, and the tip of the valve housing is pressed toward the inner wall surface of the oil passage.
- the present invention does not fix the valve housing so that it cannot move, but allows the valve housing to move, and presses the tip of the valve housing toward the inner wall surface of the oil passage by the biasing force from the biasing means. It is said. For this reason, when the oil jet switching valve is closed, there is no gap between the tip of the valve housing and the inner wall surface of the oil passage. Therefore, it is possible to ensure a good sealing property between the two, and to prevent oil leakage to the oil jet mechanism side.
- a recessed portion into which the tip of the valve housing fits may be formed in the oil passage.
- a valve body is inserted into the valve housing so as to be able to move forward and backward, and the valve body moves forward to close an opening formed in the valve housing and block the oil passage.
- a biasing force in the forward movement direction is applied to the valve main body by the biasing means, and when the valve main body moves forward, the valve main body comes into contact with a part of the inner surface of the valve housing.
- the urging force from the urging means may be applied to the valve housing.
- the urging force from the urging means is applied to the valve housing only when the oil jet switching valve is closed due to the forward movement of the valve body, and the tip of the valve housing is connected to the inner wall surface of the oil passage. It will be pressed toward. That is, the tip of the valve housing is pressed toward the inner wall surface of the oil passage in conjunction with the closing operation of the oil jet switching valve. For this reason, it is possible to set the period during which the urging force is applied to the valve housing only to the necessary period, and when the oil jet switching valve is closed, it is ensured that the tip of the valve housing faces the inner wall surface of the oil passage. Can be pressed.
- a recess having a predetermined length dimension is formed in the inner wall surface of the insertion hole in a direction along the axis of the insertion hole, while the outer wall surface of the valve housing is located in the recess.
- a protrusion having a clearance in the direction along the axis may be provided between the inner surface of the recess. That is, the valve housing may be movable along the axial center within the insertion hole by the dimension of the clearance.
- This configuration can prevent the valve housing from falling out of the insertion hole. Further, the moving range of the valve housing can be limited. For this reason, it can be avoided that the valve housing is moved more than necessary and the oil flow in the oil passage is obstructed.
- a control valve is provided for switching the hydraulic pressure for advancing and retracting the valve body inserted into the valve housing.
- the control valve is provided with a first port and a second port.
- the first port communicates with a main oil passage that supplies oil discharged from the oil pump toward the oil jet mechanism.
- the second port communicates with the back pressure space of the valve body.
- valve main body moves backward by releasing the hydraulic pressure acting on the back pressure space, thereby opening the opening. It is the structure which connects an oil path by opening.
- control valve is provided with a drain port that communicates with the second port and discharges oil in the back pressure space when the control valve is in a switching state in which the first port and the second port are shut off. May be.
- the tip of the valve housing is pressed toward the inner wall surface of the oil passage. For this reason, it becomes possible to ensure the sealing performance between the front-end
- FIG. 1 is a diagram showing a schematic configuration of an oil supply system of an engine (internal combustion engine) 1 according to the present embodiment.
- an engine 1 includes a cylinder head 11 and a cylinder block 12 constituting an engine body, an oil pan 13 attached to a lower end portion of the cylinder block 12, and internal lubrication and internal cooling of the engine 1.
- an oil supply system 2 that circulates engine oil (hereinafter also simply referred to as “oil”) in the engine 1.
- a plurality of lubricated members and cooled members such as a piston 14, a crankshaft 15 and a camshaft 16 are accommodated.
- the cylinder block 12 is formed with four cylinders. These cylinders are arranged over the cylinder arrangement direction (left-right direction in the figure).
- the piston 14 is accommodated in the cylinder so as to be reciprocally movable in the vertical direction in the figure.
- the oil stored in the oil pan 13 is sucked out from the oil pan 13 and supplied to the respective members to be lubricated and the members to be cooled. 13 is configured to be able to reflux.
- an oil strainer 31 having a suction port 31a for sucking the oil stored in the oil pan 13 is disposed.
- the oil strainer 31 is connected to an oil pump 32 provided in the cylinder block 12 via a strainer flow path 31b.
- the oil pump 32 is a known rotary pump.
- the rotor 32a of the oil pump 32 is mechanically coupled to the crankshaft 15 so as to rotate together with the crankshaft 15.
- the oil pump 32 is connected to an oil inlet of an oil filter 33 provided outside the cylinder block 12 via an oil transport path 34.
- the oil outlet of the oil filter 33 is connected to an oil supply path 35 provided as an oil flow path toward the lubricated member or the cooled member.
- the oil pump 32 may be an electric oil pump.
- the oil supply system 2 supplies the oil pumped up from the oil pan 13 via the oil strainer 31 to each member to be lubricated by the oil pump 32 to be used as lubricating oil, or to the member to be cooled such as the piston 14. It is used as cooling oil, or supplied to hydraulic operating equipment and used as hydraulic oil.
- the oil pumped from the oil pump 32 passes through the oil filter 33 and then is sent to the main oil hole (main gallery; main oil passage) 21 extending along the cylinder row direction.
- Oil passages 22 and 23 extending upward from the cylinder block 12 to the cylinder head 11 are communicated with one end side and the other end side of the main oil hole 21.
- the oil passage 22 communicated with one end side (the left side in FIG. 1) of the main oil hole 21 is further branched into a chain tensioner side passage 24 and a VVT (Variable Valve Timing) side passage 25.
- VVT Variariable Valve Timing
- the oil supplied to the chain tensioner side passage 24 is used as hydraulic oil for the chain tensioner 41 for adjusting the tension of the timing chain.
- the oil supplied to the VVT side passage 25 passes through an OCV (OilOControl Valve) oil filter 42a and is used as hydraulic oil for the VVT OCV 42b and the variable valve timing mechanisms 42 and 43.
- the oil passage 23 communicated with the other end side (right side in FIG. 1) of the main oil hole 21 is branched into a lash adjuster side passage 26 and a shower pipe side passage 27.
- the lash adjuster side passage 26 is further branched into an intake side passage 26a and an exhaust side passage 26b.
- the intake side passage 26a the lash adjusters 44, 44,... Disposed corresponding to the intake valves of the respective cylinders communicate with the oil supply passages. It has come to be used.
- the exhaust side passage 26b communicates with the oil supply passages of lash adjusters 45, 45,... Disposed corresponding to the exhaust valves of the respective cylinders, and the oil that has passed through the oil supply passages passes through the lash adjuster 45. It is used as hydraulic oil.
- the lash adjuster side passage 26 also branches and supplies oil to the journal portion of each camshaft 16. Thereby, lubrication is performed between each camshaft 16 and the journal bearing portion of the cylinder head 11 and between each camshaft 16 and a journal bearing portion of a cam cap (not shown).
- the shower pipe side passage 27 is also branched into an intake side passage 27a and an exhaust side passage 27b.
- an oil spray hole (not shown) is formed corresponding to the cam lobe of the intake camshaft.
- the oil flowing through the intake side passage 27a is sprayed from the oil spray hole toward the contact portion between the cam lobe of the intake camshaft and the roller portion of the rocker arm, and contributes to lubrication of both.
- an oil spray hole (not shown) is formed corresponding to the cam lobe of the exhaust camshaft.
- the oil flowing through the exhaust side passage 27b is sprayed from the oil spray hole to the cam lobe of the exhaust camshaft, and contributes to lubrication of both.
- the oil supply system 2 is provided with an oil jet device 5 for cooling the piston 14.
- the oil jet device 5 will be described.
- FIG. 2 is a cross-sectional view of the oil jet device 5 and its surroundings.
- FIG. 2 shows a state in which an oil jet switching valve 8 described later is closed (see FIG. 3 for a state in which the oil jet switching valve 8 is opened).
- OSV 7 described later is disposed in the horizontal direction (the axial direction is the horizontal direction)
- the hydraulic sensor 105 is disposed in the vertical direction (the axial direction is the vertical direction).
- the oil jet device 5 includes an oil jet mechanism 51 and an oil jet switching mechanism 52 provided on the upstream side of the oil jet mechanism 51.
- the oil jet mechanism 51 includes a plurality of (four in the present embodiment) piston jet nozzles (oil jet nozzles) 6, 6,... Disposed corresponding to the respective cylinders, and the oil jet switching mechanism 52.
- An oil jet gallery (oil passage) 53 is provided for supplying oil flowing from the main oil hole 21 toward the piston jet nozzle 6 when the oil jet switching valve 8 is open.
- the oil jet switching mechanism 52 includes an oil jet passage 54 communicating with the main oil hole 21, an OSV (Oil Switching Valve) 7 connected to the oil jet passage 54, and an oil jet switching valve. 8 is provided.
- OSV Oil Switching Valve
- the oil jet gallery 53 is formed inside the cylinder block 12.
- the upstream end of the oil jet gallery 53 can communicate with the main oil hole 21 via the oil jet switching mechanism 52.
- the downstream side of the oil jet gallery 53 is branched corresponding to each cylinder.
- the piston jet nozzle 6 is disposed in the vicinity of the downstream end of each of the branched oil passages.
- the piston jet nozzle 6 includes a main body portion 61 and a tubular nozzle 62 attached to the main body portion 61.
- a check ball mechanism (check valve mechanism) 63 is accommodated in the main body 61.
- the structure of the check ball mechanism 63 is formed with a through hole 61 a penetrating in the vertical direction inside the main body 61.
- the upper end opening of the through hole 61 a communicates with the oil jet gallery 53.
- the inner diameter of the through hole 61a the upper portion has a small diameter (hereinafter referred to as a small diameter portion) and the lower portion has a large diameter (hereinafter referred to as a large diameter portion). And the lower end of this small diameter part is the valve seat 61b.
- a check ball 63a capable of coming into contact with the valve seat 61b and a spring 63b made of a compression coil spring for pressing the check ball 63a toward the valve seat 61b are accommodated.
- the outer diameter of the check ball 63a is set to be larger than the inner diameter of the small diameter portion of the through hole 61a and smaller than the inner diameter of the large diameter portion.
- a plug 63c that closes the lower end opening of the through hole 61a and contacts the lower end of the spring 63b is attached to the lower end of the main body 61. Thereby, the spring 63b is compressed between the valve seat 61b and the plug 63c.
- the internal space of the nozzle 62 communicates with the large diameter portion of the through hole 61 a of the main body 61.
- the nozzle 62 extends from the main body 61 in a substantially horizontal direction and then extends substantially vertically upward, and an injection hole is formed at the upper end of the nozzle 62 toward the back surface of the piston 14.
- the check ball 63a is detached from the valve seat 61b against the urging force of the spring 63b.
- the through hole 61a is opened (open state of the check ball mechanism 63; see FIG. 3).
- the oil flowing from the oil jet gallery 53 into the through hole 61 a flows into the nozzle 62.
- the oil that has flowed into the nozzle 62 is sprayed toward the back surface of the piston 14.
- the piston 14 is cooled by this oil jet, and for example, an excessive increase in the in-cylinder temperature can be suppressed to prevent knocking.
- the value of the hydraulic pressure released by the check ball mechanism 63 is adjusted by appropriately setting the spring constant of the spring 63b.
- the oil jet flow path 54 of the oil jet switching mechanism 52 is formed inside the cylinder block 12, and the upstream end communicates with the main oil hole 21. Further, the downstream side of the oil jet passage 54 is branched into a pilot passage 54 a whose downstream end is connected to the OSV 7 and an oil jet introduction oil passage 54 b disposed substantially coaxially with the oil jet gallery 53. Yes.
- the oil jet switching valve 8 is accommodated in a valve insertion hole 81 formed in the cylinder block 12.
- the valve insertion hole 81 extends in a direction substantially orthogonal to the extending direction of the oil jet gallery 53 and the oil jet introduction oil passage 54b, and one end side (the upper end side in the figure) is in the internal space of the OSV 7. The other end side (the lower end side in the figure) communicates with the oil jet gallery 53 and the oil jet introduction oil passage 54b.
- the oil jet switching valve 8 accommodated in the valve insertion hole 81 includes a valve housing 82, a valve body 83, a collar 84, a spring (attached). Force means) 85.
- a valve housing 82 As shown in FIG. 4 (an exploded perspective view of the oil jet switching valve 8), the oil jet switching valve 8 accommodated in the valve insertion hole 81 includes a valve housing 82, a valve body 83, a collar 84, a spring (attached). Force means) 85.
- the valve housing 82 is a substantially cylindrical member inserted into the valve insertion hole 81.
- the outer diameter dimension of the valve housing 82 substantially matches the inner diameter dimension of the valve insertion hole 81.
- the valve housing 82 is movable inside the valve insertion hole 81 in a direction along the axis (vertical direction in FIG. 2).
- the length dimension of the valve housing 82 (the length dimension in the direction along the axis) is the same as the length dimension of the valve insertion hole 81 (the length dimension in the direction along the axis) and the oil jet introduction oil passage. It is set slightly shorter than the sum of the inner diameter dimension of 54b.
- an oil introduction port 82a and an oil outlet port (opening) 82b are formed on the side surface in the vicinity of the tip of the valve housing 82 so as to face each other with the shaft center of the valve housing 82 interposed therebetween.
- the oil introduction port 82a opens toward the oil jet introduction oil passage 54b.
- the axis of the oil inlet 82 a is orthogonal to the axis of the valve housing 82.
- the oil outlet 82 b opens toward the oil jet gallery 53.
- the axis of the oil outlet 82 b is also orthogonal to the axis of the valve housing 82.
- the opening area of the oil outlet 82b is set to be slightly smaller than the opening area of the oil inlet 82a.
- the axis of the oil outlet 82b is located slightly above the axis of the oil inlet 82a (see FIG. 7A).
- annular recess 81a is formed in the inner surface of the valve insertion hole 81 in the vicinity of the upper end in the drawing.
- the formation position, height dimension, and outer diameter dimension of the recess 81a are appropriately set.
- an annular protrusion 82c to be inserted into the recess 81a is formed on the outer peripheral surface of the valve housing 82.
- the thickness dimension (vertical dimension in FIG. 2) of the protrusion 82c is slightly shorter than the height dimension (vertical dimension in the figure) of the recess 81a. That is, a clearance C is provided between the projection 82c and the recess 81a in the vertical direction in the figure. For this reason, the valve housing 82 is movable within the valve insertion hole 81 in a direction along the axis (vertical direction in the drawing) by the dimension of the clearance C.
- the bottom (inner wall surface) of the oil passage at the boundary between the oil jet introduction oil passage 54b and the oil jet gallery 53 has a shape that substantially matches the shape of the tip portion (lower end portion) of the valve housing 82.
- a recessed portion 55 is formed.
- the recessed portion 55 has a substantially cylindrical shape.
- the inner diameter dimension of the recessed portion 55 substantially matches the outer diameter dimension of the distal end portion of the valve housing 82 or is set slightly larger than the outer diameter dimension. For this reason, as described above, when the valve housing 82 that is movable in the vertical direction moves downward, the tip portion of the valve housing 82 is fitted into the recessed portion 55.
- the lower surface of the projection 82c of the valve housing 82 is in contact with the bottom surface of the recess 81a of the valve insertion hole 81, or both A slight gap exists between the two.
- the protrusion 82c and the recess 81a allow the movement of the valve housing 82 to a position where the tip portion of the valve housing 82 fits into the recess 55 when the valve housing 82 moves downward. C is formed.
- an opening 82d is formed at the tip of the valve housing 82.
- Protrusions 86 and 87 projecting toward the inner peripheral side are provided on the inner peripheral edge of the opening 82d.
- the height dimension (t1 in the figure) of the protrusion 87 provided on the oil outlet 82b side is the height dimension (t2 in the figure) of the protrusion 86 provided on the oil inlet 82a side. Is set slightly longer.
- An inclined surface 87a is formed at the upper end of the inner edge of the protrusion 87 provided on the oil outlet 82b side. In a closed state of the valve main body 83 to be described later, the tip end portion of the valve main body 83 comes into contact with the inclined surface 87a.
- the formation range of the protrusion 87 on the oil outlet 82b side is set to a range of about 1/3 to 1/4 with respect to the entire circumference of the valve housing 82. This range is not limited to this, and as will be described later, an area (area of the inclined surface 87a) in which the urging force of the spring 85 is reliably transmitted to the valve housing 82 via the valve body 83 is secured. As long as it is within the range.
- the valve body 83 is a member inserted into the valve housing 82, and as shown in FIG. 7A, a cylindrical body 83a and a valve part 83b integrally formed at the lower end of the body 83a. It has a bottomed cylindrical shape with The outer diameter dimension of the body portion 83a substantially matches the inner diameter dimension of the valve housing 82. For this reason, the valve main body 83 is movable in the direction along the axis (vertical direction in the figure) inside the valve housing 82.
- the valve portion 83b includes a base portion 83c having an outer diameter that matches the outer diameter size of the body portion 83a, and a distal end portion 83d that is continuous with the lower end of the base portion 83c and has a smaller diameter than the base portion 83c. It has.
- the outer diameter of the tip 83d is larger than the inner diameter of the opening 82d formed at the tip of the valve housing 82. As described above, in the closed state of the valve body 83, the tip 83d of the valve portion 83b is in contact with the inclined surface 87a of the protrusion 87 provided on the oil outlet 82b side of the valve housing 82. It has become.
- the collar 84 is a cylindrical member inserted into the valve housing 82.
- the outer diameter of the collar 84 substantially matches the inner diameter of the valve housing 82.
- a spring seat 84 a with which the upper end edge of the spring 85 abuts is formed at the lower end portion of the collar 84. Further, the upper end surface of the collar 84 is in contact with the casing 71 of the OSV 7.
- the spring 85 is formed of a compression coil spring, and is housed in a compressed state between the upper surface of the valve portion 83 b of the valve body 83 and the spring seat 84 a of the collar 84. Therefore, a downward biasing force in the figure is applied to the valve body 83. That is, an urging force is applied in such a direction that the valve body 83 is advanced toward the boundary portion between the oil jet introduction oil passage 54 b and the oil jet gallery 53.
- the OSV 7 is accommodated in a casing 71 so that a plunger 72 can reciprocate.
- the OSV 7 switches the oil flow path by the reciprocating movement of the plunger 72 when the electromagnetic solenoid 77 is energized / de-energized.
- the casing 71 is formed with a hydraulic pressure introduction port (first port) 71a, a valve pressure port (second port) 71b, and a drain port 71c.
- the hydraulic pressure introduction port 71a is provided on the front end surface of the casing 71 and communicates with the pilot flow path 54a.
- the valve pressure port 71b is provided on the side surface (the lower surface in FIG. 2) of the casing 71 and communicates with the valve insertion hole 81 (the back pressure space of the valve body 83).
- the drain port 71c is provided on the side surface of the casing 71 on the base end side (electromagnetic solenoid 77 side) from the position where the valve pressure port 71b is formed, and communicates with a drain oil passage 12a connected to a crankcase (not shown).
- a check ball 73 is accommodated in a position corresponding to the hydraulic pressure introduction port 71a and the valve pressure port 71b in the casing 71.
- the check ball 73 communicates with the hydraulic pressure introduction port 71a and the valve pressure port 71b according to the position, and closes the hydraulic pressure introduction port 71a and the valve pressure port 71b from the drain port 71c (see FIG. 2).
- the valve pressure port 71b and the drain port 71c are in communication with each other, and the valve pressure position where the valve pressure port 71b and the drain port 71c are shut off from the hydraulic pressure introduction port 71a (see the state of FIG. 3). It is possible to move between.
- a stopper 74 is fixed on the hydraulic introduction port 71a side with respect to the accommodation position of the check ball 73.
- the stopper 74 has a hydraulic pressure introducing hole 74a that allows the hydraulic pressure introducing port 71a to communicate with the inside of the casing 71 (the accommodation space for the check ball 73).
- the inner diameter dimension of the hydraulic pressure introduction hole 74 a is set smaller than the outer diameter dimension of the check ball 73. Therefore, when the check ball 73 is in a position retracted from the stopper 74, as shown in FIG. 2, the hydraulic pressure introduction hole 74a is opened, and the hydraulic pressure introduction port 71a, the valve pressure port 71b, Will communicate. On the other hand, when the check ball 73 moves toward the stopper 74 and comes into contact with the stopper 74, the hydraulic pressure introduction hole 74a is closed as shown in FIG. The valve pressure port 71b is shut off.
- a valve seat 75 is fixed to the drain port 71c side with respect to the accommodation position of the check ball 73.
- the valve seat 75 has a drain hole 75a that communicates the drain port 71c and the inside of the casing 71 (the accommodation space for the check ball 73).
- the inner diameter of the drain hole 75a is set smaller than the outer diameter of the check ball 73. Therefore, when the check ball 73 is in a position retracted from the valve seat 75, the drain hole 75a is opened as shown in FIG. 3, and the valve pressure port 71b and the drain port 71c are connected. You will communicate.
- the check ball 73 moves toward the valve seat 75 and contacts the valve seat 75, the drain hole 75a is closed as shown in FIG. 2, and the valve pressure port 71b is closed. And the drain port 71c are shut off.
- the plunger 72 is applied with a biasing force toward the check ball 73 by a spring 76 formed of a compression coil spring, and is driven by an electromagnetic solenoid 77. That is, when no voltage is applied to the electromagnetic solenoid 77, as shown in FIG. 3, the plunger 72 moves forward in the casing 71 to the left in the figure by the urging force of the spring 76. This state is the OFF state of OSV7. On the other hand, when a voltage is applied to the electromagnetic solenoid 77, the plunger 72 moves backward in the casing 71 to the right in the figure against the urging force of the spring 76, as shown in FIG. This state is the ON state of OSV7. Application and non-application of voltage to the electromagnetic solenoid 77 are controlled by the ECU 100 (see FIG. 5).
- the plunger 72 does not press the check ball 73 as shown in FIG.
- the check ball 73 receives the hydraulic pressure from the pilot flow path 54 a
- the check ball 73 moves backward from the stopper 74 and comes into contact with the valve seat 75.
- the hydraulic pressure introduction port 71a and the valve pressure port 71b communicate with each other.
- the hydraulic pressure from the main oil hole 21 through the pilot flow path 54 a is introduced into the valve insertion hole 81.
- the valve body 83 is provided with a spring 85 provided on the back surface side.
- valve body 83 It moves toward the oil jet introduction oil passage 54b by the force (moves downward in the figure).
- the valve body 83 closes the oil outlet 82b of the valve housing 82, and the outer edge of the tip 83d of the valve body 83 is located on the oil outlet 82b side of the valve housing 82. It contacts the inclined surface 87a of the protrusion 87. Due to this contact, the valve housing 82 also receives a biasing force from the spring 85, and the valve housing 82 moves forward toward the recessed portion 55, and as shown in FIG. The part fits into the recessed part 55. As a result, the downstream end of the oil jet introduction oil passage 54b is closed by the oil jet switching valve 8, and no oil is supplied to the oil jet gallery 53 of the oil jet mechanism 51, and the oil jet is stopped.
- the oil jet switching valve 8 since the oil pressure from the main oil hole 21 is acting on the front end surface of the valve body 83 of the oil jet switching valve 8, the oil jet switching valve 8 is provided with a biasing force of a spring 85 provided on the back side thereof. Against the inside of the valve insertion hole 81 (moves upward in the figure). As the valve main body 83 moves, the valve main body 83 opens the oil outlet port 82b of the valve housing 82, and the oil jet introduction oil passage 54b and the oil jet gallery 53 are communicated with each other. Oil is supplied to the oil jet gallery 53. When the oil pressure supplied to the oil jet gallery 53 reaches a predetermined value as the engine speed increases, the check ball mechanism 63 of the piston jet nozzle 6 is opened, and the oil jet is executed. The piston 14 is cooled.
- the oil jet switching valve 8 is opened and closed by switching the hydraulic pressure inside the valve insertion hole 81 in conjunction with the switching operation of the OSV 7. For this reason, this OSV 7 needs only to have a function of switching the oil supply passage, and can be realized as a relatively small one. As a result, the oil jet switching mechanism 52 is reduced in size. Further, when the oil jet switching valve 8 is moved backward, the hydraulic pressure in the valve insertion hole 81 is lowered. For this reason, the backward movement of the oil jet switching valve 8 is started almost simultaneously with the switching of the OSV 7, and the controllability is good.
- the cooling of the piston 14 is mainly intended to prevent the occurrence of knocking in the combustion stroke of the engine 1. For this reason, basically, when the engine 1 is warming up, the demand for cooling the piston 14 is low, and after the warming up of the engine 1 is completed (particularly, in a high-load operating range or high rotation Area), the demand for cooling the piston 14 increases. For this reason, for example, at the initial stage of the cold start of the engine 1, since the coolant temperature is relatively low, the request for cooling the piston 14 is low, the OSV 7 is turned on, and the oil jet is stopped.
- the OSV 7 is turned off, and engine oil is supplied to the oil jet gallery 53, and each piston jet nozzle The engine oil is injected from 6, 6,... Toward the back surfaces of the pistons 14, 14,.
- FIG. 5 is a block diagram showing a control system according to OSV7.
- the ECU 100 is an electronic control device that executes operation control of the engine 1 and the like.
- the ECU 100 includes a CPU (Central Processing Unit), a ROM (Read Only Memory), a RAM (Random Access Memory), a backup RAM, and the like.
- CPU Central Processing Unit
- ROM Read Only Memory
- RAM Random Access Memory
- the ROM stores various control programs, maps that are referred to when the various control programs are executed, and the like.
- the CPU executes arithmetic processing based on various control programs and maps stored in the ROM.
- the RAM is a memory for temporarily storing calculation results in the CPU, data input from each sensor, and the like.
- the backup RAM is a non-volatile memory that stores data to be saved when the engine 1 is stopped.
- a plurality of sensors are connected to the ECU 100.
- the crank position sensor 101 that transmits a pulse signal every time the crankshaft 15 that is the output shaft of the engine 1 rotates by a predetermined angle
- the air flow meter 102 that detects the intake air amount, and the depression amount of the accelerator pedal.
- An accelerator opening sensor 103 that detects the accelerator opening
- a water temperature sensor 104 that detects the temperature of engine coolant
- a hydraulic sensor 105 that detects the oil pressure inside the main oil hole 21, and the like are connected to the ECU 100. Signals from these sensors 101 to 105 are input to the ECU 100.
- the oil pressure sensor 105 is attached to the main oil hole 21 and detects the oil pressure inside the main oil hole 21.
- the ECU 100 includes, as well-known sensors, an oil temperature sensor, a throttle opening sensor, a wheel speed sensor, a shift position sensor, a brake pedal sensor, an intake air temperature sensor, an A / F sensor, and an O 2 sensor.
- a cam position sensor or the like (all not shown) is connected, and signals from these sensors are also input.
- the ECU 100 performs control of various actuators (throttle motor, injector, igniter, etc.) of the engine 1 and control of opening / closing of the OSV 7 (oil jet control) based on output signals of various sensors. .
- the OSV 7 is turned on and the oil jet is stopped during a period when a predetermined oil jet stop condition is satisfied.
- This oil jet stop condition is satisfied, for example, when the engine rotation speed is equal to or lower than a predetermined speed and the engine load is equal to or lower than a predetermined value.
- FIG. 6 shows an oil jet execution map stored in the ROM of the ECU 100.
- an oil jet execution area and an oil jet stop area are set using the engine speed and the engine load as parameters. That is, when the engine rotation speed is Ne1 or less in the figure and the engine load is KL1 or less in the figure, the oil jet stop signal is output from the ECU 100, assuming that the engine operation area is in the oil jet stop area, The OSV 7 is turned on to stop the oil jet.
- the engine rotation speed exceeds Ne1 in the figure or when the engine load exceeds KL1 in the figure, it is determined that the engine operation area is in the oil jet execution area and the ECU 100 An execution signal is output and the OSV 7 is turned off to execute the oil jet.
- the values of the engine rotation speed Ne1 and the engine load KL1 are set by experiments or simulations. For example, each value is set so that knocking does not occur in the combustion stroke of the engine 1 and the temperature of the piston 14 is appropriately maintained (so that the piston 14 is not overcooled).
- the OSV 7 When a predetermined oil jet stop condition is satisfied and an oil jet stop signal is output from the ECU 100, the OSV 7 is turned on as described above, and the valve body 83 is moved to the spring 85 as shown in FIG. 7A. The urging force moves toward the oil jet introduction oil passage 54b (moves downward in the figure). Along with the movement of the valve body 83, the valve body 83 closes the oil outlet 82b of the valve housing 82, and the outer edge of the tip 83d of the valve body 83 is located on the oil outlet 82b side of the valve housing 82. It contacts the inclined surface 87a of the protrusion 87.
- valve housing 82 Due to this contact, the valve housing 82 also receives a biasing force from the spring 85, and the valve housing 82 moves forward toward the recessed portion 55. Then, the tip end portion of the valve housing 82 is pressed toward the bottom surface of the recessed portion 55. Therefore, a good sealing property is ensured between the front end surface of the valve housing 82 and the bottom surface of the recessed portion 55, and the piston jet nozzle 6 side is formed between the front end surface of the valve housing 82 and the bottom surface of the recessed portion 55. Oil is prevented from leaking out.
- valve housing 82 is movable in the direction along the axis by the clearance C (clearance C between the protrusion 82c and the recess 81a), not only can the valve housing 82 be prevented from coming off.
- the moving range of the valve housing 82 can be limited. For this reason, it can be avoided that the valve housing 82 is moved more than necessary and the oil flow in the oil passage is obstructed.
- valve housing 82 is different from that of the above embodiment. Since other configurations and operations are the same as those of the above-described embodiment, only the configuration of the valve housing 82 will be described here.
- the oil jet switching valve 8 has a configuration in which a sealing material 88 is attached to the tip surface of the valve housing 82.
- the seal member 88 is attached from the front end surface of the valve housing 82 to the side surface of the front end portion of the valve housing 82 by means such as adhesion.
- the sealing material 88 is made of rubber or resin, and the material is not particularly limited as long as it has elasticity.
- the present invention is applied to an in-line four-cylinder gasoline engine has been described.
- the number of cylinders and the type of engine (V type, horizontally opposed type, etc.) are not particularly limited.
- the present invention can also be applied to a diesel engine.
- the OSV 7 is provided in the oil jet switching mechanism 52.
- the present invention is not limited to this, and an OCV (Oil Control Valve) whose opening degree can be adjusted may be provided.
- the present invention is applied to a conventional vehicle (a vehicle equipped with only the engine 1 as a driving force source) has been described.
- a hybrid vehicle an engine and an electric motor are mounted as a driving force source
- the present invention can also be applied to a vehicle.
- the oil jet device 5 has been described as an example of a device that can be switched between supply and non-supply of engine oil.
- the present invention is not limited to this, and can also be applied to an apparatus that switches between supply and non-supply of engine oil to a cam shower or a timing chain jet. That is, the present invention is applied when switching between supply and non-supply of engine oil to the shower pipe side passage 27 and when switching between supply and non-supply of engine oil to a timing chain jet (not shown).
- These devices are designed to supply the engine oil by turning off the OSV and opening the oil jet switching valve in a situation where the engine speed is lower than the predetermined speed and lubrication due to scattering of engine oil cannot be performed. is there.
- the present invention can be applied to a seal structure of a mechanism for switching between execution and stop of an oil jet in an oil jet device.
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Abstract
Description
図1は、本実施形態に係るエンジン(内燃機関)1のオイル供給系統の概略構成を示す図である。この図1に示すように、エンジン1は、エンジン本体を構成するシリンダヘッド11およびシリンダブロック12と、このシリンダブロック12の下端部に取り付けられたオイルパン13と、エンジン1の内部潤滑や内部冷却等のためのエンジンオイル(以下、単に「オイル」という場合もある)をエンジン1内で循環させるオイル供給系統2とを備えている。
前記オイル供給系統2には、ピストン14を冷却するためのオイルジェット装置5が備えられている。以下、このオイルジェット装置5について説明する。
前記オイルジェットギャラリ53は、前記シリンダブロック12の内部に形成されている。このオイルジェットギャラリ53の上流端は、前記オイルジェット切り換え機構52を介してメインオイルホール21に連通可能となっている。また、このオイルジェットギャラリ53の下流側は各気筒に対応して分岐している。この分岐された油路それぞれの下流端近傍には前記ピストンジェットノズル6が配設されている。これにより、前記オイルジェット切り換え機構52のオイルジェット切り換えバルブ8が開放状態にある際(図3を参照)には、前記メインオイルホール21からオイルジェット切り換え機構52を経てオイルジェットギャラリ53に向けてオイルが供給されるようになっている(オイルジェット切り換え機構52におけるオイルジェット切り換えバルブ8の開閉動作については後述する)。
前記オイルジェット切り換え機構52のオイルジェット流路54は、前記シリンダブロック12の内部に形成されており、上流端が前記メインオイルホール21に連通している。また、このオイルジェット流路54の下流側は、下流端がOSV7に繋がるパイロット流路54aと、前記オイルジェットギャラリ53と略同軸上に配設されたオイルジェット導入油路54bとに分岐されている。
バルブハウジング82は、前記バルブ挿入孔81に挿入された略円筒形状の部材である。このバルブハウジング82の外径寸法はバルブ挿入孔81の内径寸法に略一致している。このため、このバルブハウジング82は、バルブ挿入孔81の内部において、その軸心に沿う方向(図2における上下方向)に移動自在となっている。また、このバルブハウジング82の長さ寸法(軸心に沿う方向の長さ寸法)は、前記バルブ挿入孔81の長さ寸法(軸心に沿う方向の長さ寸法)と前記オイルジェット導入油路54bの内径寸法との和よりも僅かに短く設定されている。
バルブ本体83は、前記バルブハウジング82の内部に挿入される部材であって、図7Aに示すように、円筒形状の胴部83aと、この胴部83aの下端に一体形成された弁部83bとを有した有底円筒形状となっている。胴部83aの外径寸法は前記バルブハウジング82の内径寸法に略一致している。このため、このバルブ本体83はバルブハウジング82の内部において、その軸心に沿う方向(図中の上下方向)に移動自在となっている。また、前記弁部83bの構成としては、前記胴部83aの外径寸法に一致する外径を有する基部83cと、この基部83cの下端に連続し、この基部83cよりも小径の先端部83dとを備えている。また、この先端部83dの外径寸法は、前記バルブハウジング82の先端部に形成されている前記開口82dの内径寸法よりも大径となっている。そして、前述した如く、バルブ本体83の閉鎖状態では、この弁部83bの先端部83dが、前記バルブハウジング82におけるオイル導出口82b側に設けられている突部87の傾斜面87aに当接する構成となっている。また、この弁部83bの先端部83dが前記傾斜面87aに当接した状態にあっては、弁部83bの先端部83dと前記オイル導入口82a側の突部86との間に隙間が生じている。これにより、この弁部83bの先端部83dに前記メインオイルホール21およびオイルジェット導入油路54bの油圧が作用する構成となっている。この油圧は、弁部83bの先端部83dに対して垂直方向に作用して、前記バルブ本体83を後退移動(図中の上方へ移動)させる力として作用することになる。
カラー84は、前記バルブハウジング82の内部に挿入される円筒形状の部材である。このカラー84の外径寸法はバルブハウジング82の内径寸法に略一致している。また、このカラー84の下端部には、前記スプリング85の上端縁が当接するスプリング座84aが形成されている。また、このカラー84の上端面は、前記OSV7のケーシング71に当接されている。
スプリング85は、圧縮コイルバネで成り、前記バルブ本体83の弁部83bの上面とカラー84のスプリング座84aとの間に圧縮された状態で収容されている。このため、バルブ本体83には、図中下向きの付勢力が付与されている。つまり、このバルブ本体83を前記オイルジェット導入油路54bとオイルジェットギャラリ53との境界部分に向かって前進させる方向の付勢力が付与されている。このため、バルブ本体83の背圧とオイルジェット導入油路54bの内圧(弁部83bの先端部83dに作用する油圧)とが略同一になった場合には、このスプリング85の付勢力によってバルブ本体83がオイルジェット導入油路54b側へ前進移動し、バルブハウジング82のオイル導出口82bを閉鎖する。これにより、オイルジェット導入油路54bとオイルジェットギャラリ53との間が遮断されることになる(オイルジェット切り換えバルブ8の閉鎖状態;図2の状態を参照)。一方、オイルジェット導入油路54bの内圧(弁部83bの先端部83dに作用する油圧)が、バルブ本体83の背圧とスプリング85の付勢力との和よりも高くなった場合には、このスプリング85の付勢力に抗してバルブ本体83がオイルジェット導入油路54bから後退する方向に移動し(バルブ挿入孔81の内部に引き込まれ)、バルブハウジング82のオイル導出口82bを開放する。これにより、オイルジェット導入油路54bとオイルジェットギャラリ53との間が連通されることになる(オイルジェット切り換えバルブ8の開放状態;図3の状態を参照)。
前記OSV7は、ケーシング71内にプランジャ72が往復移動可能に収容されている。このOSV7は、電磁ソレノイド77の通電/非通電に伴うプランジャ72の往復移動によってオイルの流路を切り換える。
図5は、前記OSV7に係る制御系を示すブロック図である。ECU100は、エンジン1の運転制御などを実行する電子制御装置である。ECU100は、CPU(Central Processing Unit)、ROM(Read Only Memory)、RAM(Random Access Memory)およびバックアップRAMなどを備えている。
次に、変形例について説明する。この変形例は、バルブハウジング82の構成が前記実施形態のものと異なっている。他の構成および動作は前記実施形態のものと同様であるので、ここではバルブハウジング82の構成についてのみ説明する。
以上、本発明の実施形態および変形例を図面に基づいて詳細に説明したが、これらはあくまでも一実施形態であり、本発明は当業者の知識に基づいて種々の変更、改良を加えた態様で実施することができる。
21 メインオイルホール(メインオイル通路)
32 オイルポンプ
5 オイルジェット装置
51 オイルジェット機構
53 オイルジェットギャラリ(油路)
54b オイルジェット導入油路(油路)
55 凹陥部
6 ピストンジェットノズル(オイルジェットノズル)
7 OSV(制御バルブ)
71a 油圧導入ポート(第1ポート)
71b バルブ圧力ポート(第2ポート)
71c ドレンポート
8 オイルジェット切り換えバルブ
81 バルブ挿入孔(背圧空間)
81a 凹部
82 バルブハウジング
82a オイル導入口
82b オイル導出口(開口)
82c 突起
83 バルブ本体
83d 先端部
85 スプリング(付勢手段)
87 突部
87a テーパ面
C クリアランス
Claims (7)
- オイルジェット機構に連通する油路を開閉するオイルジェット切り換えバルブを有する内燃機関のオイルジェット装置において、
前記オイルジェット切り換えバルブは、前記油路の延長方向に対して略直交する方向に延びる挿入孔に挿入され且つこの挿入孔の延長方向に沿って移動自在とされたバルブハウジングを備えており、
前記オイルジェット切り換えバルブの閉弁時、付勢手段からの付勢力を受けることによって前記バルブハウジングの先端部が前記油路の内壁面に向けて押圧される構成となっていることを特徴とする内燃機関のオイルジェット装置。 - 請求項1記載の内燃機関のオイルジェット装置において、
前記油路には、前記バルブハウジングの先端部が嵌り込む凹陥部が形成されていることを特徴とする内燃機関のオイルジェット装置。 - 請求項1または2記載の内燃機関のオイルジェット装置において、
前記バルブハウジングの内部にはバルブ本体が進退移動自在に挿入されており、このバルブ本体が前進移動することによって、前記バルブハウジングに形成されている開口を閉鎖して油路を遮断する一方、前記バルブ本体が後退移動することによって、前記開口を開放して油路を連通させるようになっており、
前記バルブ本体は、前記付勢手段によって前進移動方向への付勢力を受けており、このバルブ本体が前進移動した際に、このバルブ本体が前記バルブハウジングの内面の一部に当接することにより、前記付勢手段からの付勢力をバルブハウジングに付与する構成となっていることを特徴とする内燃機関のオイルジェット装置。 - 請求項1または2記載の内燃機関のオイルジェット装置において、
前記挿入孔の内壁面には、この挿入孔の軸心に沿う方向に所定長さ寸法を有する凹部が形成されている一方、前記バルブハウジングの外壁面には、前記凹部内に位置し且つこの凹部の内面との間に前記軸心に沿う方向のクリアランスを有する突起が設けられており、前記クリアランスの寸法だけ前記バルブハウジングは前記挿入孔の内部において前記軸心に沿って移動自在とされていることを特徴とする内燃機関のオイルジェット装置。 - 請求項3記載の内燃機関のオイルジェット装置において、
前記挿入孔の内壁面には、この挿入孔の軸心に沿う方向に所定長さ寸法を有する凹部が形成されている一方、前記バルブハウジングの外壁面には、前記凹部内に位置し且つこの凹部の内面との間に前記軸心に沿う方向のクリアランスを有する突起が設けられており、前記クリアランスの寸法だけ前記バルブハウジングは前記挿入孔の内部において前記軸心に沿って移動自在とされていることを特徴とする内燃機関のオイルジェット装置。 - 請求項3記載の内燃機関のオイルジェット装置において、
前記バルブハウジングの内部に挿入されたバルブ本体を進退移動させるための油圧を切り換える制御バルブが設けられ、
この制御バルブは、オイルポンプから吐出されたオイルをオイルジェット機構に向けて供給するメインオイル通路に連通する第1ポート、および、前記バルブ本体の背圧空間に連通する第2ポートを備えており、
前記制御バルブが第1ポートと第2ポートとを連通させる切り換え状態にある場合には、前記背圧空間にメインオイル通路からの油圧が作用することによって前記バルブ本体が前進移動して前記バルブハウジングに形成されている開口を閉鎖することにより油路を遮断する一方、前記制御バルブが第1ポートと第2ポートとを遮断する切り換え状態にある場合には、前記背圧空間に作用する油圧が解除されることによって前記バルブ本体が後退移動して前記開口を開放することにより油路を連通させる構成となっていることを特徴とする内燃機関のオイルジェット装置。 - 請求項6記載の内燃機関のオイルジェット装置において、
前記制御バルブには、前記第1ポートと第2ポートとを遮断する切り換え状態にある場合に、前記第2ポートに連通して前記背圧空間のオイルを排出するドレンポートが設けられていることを特徴とする内燃機関のオイルジェット装置。
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US14/439,877 US9828900B2 (en) | 2012-12-27 | 2013-08-28 | Oil jet apparatus of internal combustion engine |
DE112013006299.2T DE112013006299T5 (de) | 2012-12-27 | 2013-08-28 | Ölstrahlvorrichtung einer Brennkraftmaschine |
CN201380068441.9A CN104884757B (zh) | 2012-12-27 | 2013-08-28 | 内燃机的机油喷射装置 |
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JP6142885B2 (ja) * | 2015-03-05 | 2017-06-07 | マツダ株式会社 | エンジンのオイル供給装置、エンジンの製造方法及びエンジンの給油路構造 |
EP3225799A1 (en) * | 2016-04-01 | 2017-10-04 | HUSCO Automotive Holdings LLC | Pilot operated piston oil cooling jet control valve |
JP6829869B2 (ja) * | 2016-11-09 | 2021-02-17 | 荻野工業株式会社 | オイルジェット装置 |
CN111852607B (zh) * | 2017-12-13 | 2022-07-22 | 汉斯延森注油器公司 | 阀系统及其应用 |
US10590830B1 (en) * | 2018-10-23 | 2020-03-17 | GM Global Technology Operations LLC | Internal combustion engine including piston cooling jets |
EP3987161A4 (en) | 2019-08-08 | 2023-08-09 | Cummins, Inc. | PASSIVE PISTON COOLING NOZZLE CONTROL WITH SLOW WARM UP PROTECTION |
US11506110B2 (en) * | 2020-05-18 | 2022-11-22 | Schaeffler Technologies AG & Co. KG | Oil-spray tube with poppet valve |
CN115614125A (zh) * | 2022-09-07 | 2023-01-17 | 赛力斯集团股份有限公司 | 可变排量的机油泵控制方法 |
JP7364003B1 (ja) | 2022-09-26 | 2023-10-18 | いすゞ自動車株式会社 | 制御装置、制御方法及びプログラム |
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- 2013-08-28 WO PCT/JP2013/072980 patent/WO2014103429A1/ja active Application Filing
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JP2003097269A (ja) * | 2001-09-25 | 2003-04-03 | Toyota Motor Corp | 内燃機関のピストン温度制御装置 |
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CN104884757B (zh) | 2017-07-14 |
CN104884757A (zh) | 2015-09-02 |
JP2014126039A (ja) | 2014-07-07 |
US9828900B2 (en) | 2017-11-28 |
DE112013006299T5 (de) | 2015-09-10 |
JP5730846B2 (ja) | 2015-06-10 |
US20150292390A1 (en) | 2015-10-15 |
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