WO2011070604A1 - Dispositif d'alimentation en huile lubrifiante pour moteur - Google Patents

Dispositif d'alimentation en huile lubrifiante pour moteur Download PDF

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Publication number
WO2011070604A1
WO2011070604A1 PCT/JP2009/006654 JP2009006654W WO2011070604A1 WO 2011070604 A1 WO2011070604 A1 WO 2011070604A1 JP 2009006654 W JP2009006654 W JP 2009006654W WO 2011070604 A1 WO2011070604 A1 WO 2011070604A1
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WO
WIPO (PCT)
Prior art keywords
oil
lubricating oil
engine
temperature
valve
Prior art date
Application number
PCT/JP2009/006654
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English (en)
Japanese (ja)
Inventor
傍士武
中島光雄
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株式会社Tbk
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社Tbk filed Critical 株式会社Tbk
Priority to US13/514,466 priority Critical patent/US9188031B2/en
Priority to CN2009801623473A priority patent/CN102597440A/zh
Priority to PCT/JP2009/006654 priority patent/WO2011070604A1/fr
Priority to JP2011544973A priority patent/JPWO2011070604A1/ja
Priority to EP09852004.2A priority patent/EP2511490A4/fr
Publication of WO2011070604A1 publication Critical patent/WO2011070604A1/fr

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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
    • F01M1/16—Controlling lubricant pressure or quantity

Definitions

  • the present invention relates to an engine lubricating oil supply device that supplies lubricating oil to an engine.
  • lubricating oil engine oil stored in an oil pan is supplied (pumped) by a lubricating oil supply device such as an oil pump for the purpose of lubricating and cooling each part of the engine.
  • a lubricating oil supply device such as an oil pump for the purpose of lubricating and cooling each part of the engine.
  • turbocharging is performed from the low rotation range.
  • lubrication and cooling of the turbo that is effective from the low rotation range, as well as pistons that generate high torque and generate heat Oil cooling with a dedicated cooling jet is inevitable.
  • the amount of lubricating oil supplied to each part of the engine from the lubricating oil supply device that has been conventionally required mainly in the high engine speed range has become necessary from the low engine speed range.
  • the oil pump discharge flow rate is increased by increasing the size and speed of the oil pump.
  • the specifications of the oil pump determine the discharge pressure and the amount of oil discharged based on the minimum engine speed.
  • the oil pump rotates in proportion to the engine speed and lubricates from the oil pump.
  • the amount of oil discharged increases in proportion to the number of revolutions.
  • the flow rate of the lubricating oil required for engine lubrication is not necessarily proportional to the engine speed, and an excessive amount of work is generated in the oil pump at high engine speeds, increasing the engine load. Yes.
  • the oil amount adjustment valve is driven based on the electrical control by the controller (ECU), and the lubricating oil discharged from the oil pump
  • a lubricating oil supply apparatus configured to relieve a part of the engine and supply lubricating oil corresponding to a required amount corresponding to the number of revolutions of the engine to each part of the engine (see, for example, Patent Document 1).
  • the lubricating oil supply device described in Patent Document 1 also discloses a configuration that adjusts the amount of oil supplied to the engine according to the oil temperature of the lubricating oil detected by the oil temperature detector. Since this is due to electrical control by the controller, there is a problem that the configuration becomes complicated, and it is difficult to secure a space including the control system and the manufacturing cost increases.
  • the present invention has been made in view of the above-described problems, and has a simple configuration and an engine lubricating oil supply device that does not unnecessarily increase the drive loss of an oil pump even at a low temperature start of the engine.
  • the purpose is to provide.
  • an engine lubricating oil supply device includes an oil pump that is driven by an engine and sucks lubricating oil stored in an oil pan and supplies the lubricating oil to an engine lubricating portion.
  • Engine oil supply device comprising an oil amount adjusting valve for leading a part of the lubricating oil supplied to the oil pump to the first drain oil passage from the relief hole connected to the discharge port of the oil pump and draining to the oil pan
  • the oil amount adjusting valve includes a casing having a piston chamber communicating with the relief hole, and a piston member that is slidably disposed in the piston chamber and opens and closes the first drain oil passage (for example, the piston in the embodiment).
  • first urging means for example, a valve spring 39 in the embodiment
  • first urging means for example, a valve spring 39 in the embodiment
  • an orifice that is formed in the piston member and communicates between the front side space and the back side space of the piston member in the piston chamber, and a valve hole that communicates between the accommodation space formed inside and the back side space (for example, the embodiment)
  • a valve body for example, a ball in the embodiment
  • a second urging means for example, the spring unit 50 in the embodiment for urging the valve body toward the valve hole side in the valve closing direction by an urging force according to the oil temperature of the lubricating oil.
  • the engine lubricating oil supply device opens and closes the valve hole by the valve body by a balance between the urging force of the second urging means that changes according to the oil temperature of the lubricating oil and the oil pressure of the lubricating oil flowing into the rear side space.
  • the piston member By operating and draining the lubricating oil flowing into the accommodating space from the valve hole from the second drain oil passage, the front side space and the back side space generated according to the flow of the lubricating oil passing through the orifice Based on the balance between the pressure difference and the urging force of the first urging means, the piston member is slid to adjust the opening of the first drain oil passage.
  • the second urging means senses the oil temperature of the lubricating oil directly or indirectly and applies an urging force corresponding to the sensed temperature to the valve body.
  • the second urging means that changes in accordance with the pressure of the lubricating oil supplied to the engine lubricating portion from the oil pump driven in conjunction with the engine and the oil temperature of the lubricating oil. Based on the balance with the urging force, the operating pressure of the oil amount adjusting valve for opening the drain oil passage of the lubricating oil can be adjusted. For this reason, the amount of lubricating oil to be relieved out of the lubricating oil supplied from the oil pump to the engine can be appropriately adjusted according to the rotational speed of the oil pump and the oil temperature of the lubricating oil.
  • the resultant force of the biasing force of the shape memory spring and the bias spring according to the sensed temperature is applied to the valve body, so that the valve body is not affected by the oil temperature of the lubricating oil.
  • the urging force in the valve closing direction can be applied reliably. For example, even when the biasing force of the shape memory spring for closing the valve hole is very small when the sensed temperature is low, the valve hole is opened and closed mainly by the biasing force of the bias spring when the oil temperature is low. When the oil temperature is high, the opening / closing of the valve hole can be adjusted by the resultant force of the urging force of the shape memory spring and the bias spring. Therefore, the appropriate drain amount of the lubricating oil can be adjusted.
  • the engine lubricating oil supply apparatus 1 sucks lubricating oil stored in an oil pan (lubricating oil tank) provided in a vehicle (not shown) and discharges it to a lubricating oil path connected to each part of the engine (engine lubricating part).
  • the engine lubricating oil supply device 1 includes an oil pump 10 and an oil amount adjustment valve 20.
  • the oil pump 10 includes a drive gear 13 and a driven gear 14 that are rotatably provided around rotation axes parallel to each other and are externally meshed, and the drive gear 13 and the driven gear 14 are in sliding contact with the tooth tips and both side surfaces. It is a circumscribing gear pump configured to include a casing 11 having a pump chamber 12 that is housed and held in a closed state.
  • the drive gear 13 has a rotation shaft connected to the engine output shaft via a transmission gear (not shown) and the like, and the rotation drive force of the engine output shaft is transmitted to the rotation shaft.
  • the driven gear 14 are engaged with each other in the direction of the arrow in the figure. Note that the rotation shafts of the drive gear 13 and the driven gear 14 are rotatably supported by the casing 11 via a bearing (not shown) disposed in the casing 11. Both gears 13 and 14 are involute tooth type spur gears, and are formed in the same cross-sectional shape.
  • a suction hole 15 and a discharge hole 16 are formed continuously to the pump chamber 12.
  • the suction hole 15 is connected to an oil pan T, and the discharge hole 16 is connected to a lubricating oil passage of the engine. .
  • a relief hole 21 extending in a direction perpendicular to the discharge hole 16 is formed on the side surface of the discharge hole 16 in the casing 11, and the relief hole 21 is formed between the discharge hole 16 and the oil amount adjusting valve 20.
  • the piston chamber 31 is connected in communication.
  • the oil amount adjustment valve 20 is mainly composed of an opening / closing valve 30 connected to the relief hole 21 and a switching valve 40 connected to the opening / closing valve 30. First, the configuration of the switching valve 40 will be described.
  • the switching valve 40 includes a housing 41 provided in the casing 11, a cap member 48 that closes the open end of the housing 41, and a shape memory spring 51 and a bias spring 52 that are coaxially supported by the cap member 48 in the casing 11. And a ball valve body 53 supported by both springs 51 and 52.
  • the housing 41 is formed in a stepped cylindrical shape integrally having a small diameter portion 42 and a large diameter portion 43 extending in the cylindrical axis direction, and a plurality of male screws formed on the outer periphery of the small diameter portion 42 are attached to the casing 11. It is fixed to the casing 11 by being screwed into a female screw.
  • a substantially cylindrical accommodation space 44 for disposing the ball valve body 53 and the like is formed inside the housing 41, and a connection hole for connecting and connecting the accommodation space 44 and the piston chamber 31 of the on-off valve 30.
  • second drain oil passages 46 and 46 are formed to connect the accommodation space 44 and the oil pan T in communication.
  • a piston receiving portion 47 capable of abutting and supporting the piston 35 of the on-off valve 30 is formed on the distal end side of the small diameter portion 42 so as to protrude in the axial direction.
  • the cap member 48 includes a base portion 48a fitted to an end portion of the housing 41 and a rod-shaped stopper portion 48b extending in the axial direction from the base portion 48a.
  • the springs 51 and 52 are supported coaxially in a state of being inserted through the stopper portion 48b.
  • the spring unit 50 includes a shape memory spring 51 and a bias spring 52.
  • the shape memory spring 51 is formed in a coil spring shape using, for example, a Ni—Ti-based shape memory alloy whose elastic coefficient changes with temperature, and has a constant spring constant up to a predetermined temperature (transformation temperature). When the temperature is equal to or higher than a predetermined temperature (transformation temperature), the spring constant changes (increases) according to the temperature and deforms in the extension direction.
  • the bias spring 52 is a coil spring having a substantially constant spring constant regardless of the temperature, and is disposed inside the shape memory spring 51.
  • the shape memory spring 51 senses the temperature of the lubricating oil directly or indirectly and changes its own spring constant.
  • the accommodation space 44 is in communication with the oil pan T via the second drain oil passage 46, and the oil temperature of the lubricating oil stored in the oil pan T (atmospheric temperature in the oil pan T) is reached. Accordingly, the ambient temperature in the accommodation space 44 also changes. Further, the ball valve body 52 described later is always exposed to the lubricating oil flowing into the piston chamber 31, and the heat of this lubricating oil is transferred to the shape memory spring 51. Therefore, the shape memory spring 51 indirectly senses the oil temperature of the lubricating oil and changes the spring constant by the ambient temperature in the accommodation space 44 and the heat conduction from the ball valve body 53.
  • the connecting hole 45 is opened by the movement of the ball valve body 53, the lubricating oil in the piston chamber 31 flows into the receiving space 44 from the connecting hole 45, and the lubricating oil flows in the receiving space 44.
  • the shape memory spring 51 can receive heat transfer from the lubricating oil by opening the connection hole 45, and can directly sense the oil temperature of the lubricating oil and change the spring constant.
  • the ball valve body 53 is formed into a spherical shape using, for example, a metal material having high thermal conductivity.
  • the ball valve body 53 is supported by the spring unit 50 in the accommodation space 44 and is urged by the spring unit 50 in one direction (a direction in which the connection hole 45 is closed) along the axial direction.
  • the bias spring 52 is interposed between the ball valve body 52 and the cap member 48 in a predetermined compression state, the ball valve body 53 is always moved to the closed position side (connection hole 45 by a constant biasing force). Side).
  • the shape memory spring 51 expands and increases the spring constant, and the ball valve body 53 along with the bias spring 52 in one direction along the axial direction (direction in which the connecting hole 45 is closed). A biasing force is applied to.
  • the spring unit 50 appropriately determines the resultant force of the urging forces of the springs 51 and 52 according to the sensed temperature of the shape memory spring 51 (by sensing the oil temperature of the lubricating oil directly or indirectly).
  • the resultant force is applied to the ball valve body 53. Therefore, the connection hole 45 of the switching valve 40 is normally closed at the outer peripheral surface of the ball valve body 53 by the action of the spring unit 50.
  • the on-off valve 30 is formed in a piston chamber 31 formed as a cylindrical inner space in the casing 11, and in a direction close to and away from the relief hole 21 in the piston chamber 31 (left and right in FIGS. 1 and 2).
  • the piston 35 is slidably provided (in the direction), and a valve spring 39 interposed between the piston 35 and the housing 41.
  • the piston chamber 31 is connected to the relief hole 21 in the casing 11, and a first drain oil passage 34 connected to the oil pan T is formed on the side surface portion.
  • the first drain oil passage 34 is closed by the outer peripheral surface of the piston 35 in the closed position.
  • the piston 35 is integrally formed from a disk-shaped front plate portion 36 and a cylindrical outer plate portion 37, and is formed in a bottomed cylindrical shape that opens in one axial direction (rightward in FIG. 1).
  • the piston 35 partitions the interior of the piston chamber 31 into an upstream chamber 32 and a downstream chamber 33.
  • An orifice 38 penetrating in the axial direction is formed in the front plate portion 36 of the piston 35, and the relief hole 21 and the downstream chamber 33 are always in communication with each other by the orifice 38.
  • valve spring 39 One end portion of the valve spring 39 is supported by the front end portion 36 of the piston 35 and the other end portion is supported by the small diameter portion 42 of the housing 41, and the piston 35 is closed to the relief hole 21 side in the piston chamber 31. Is always energized.
  • the engine lubricant supply device 1 is in the initial state shown in FIG. 1 when the engine is stopped.
  • the urging force of the valve spring 39 is acting on the piston 35, the piston 35 is held in the closed position in the piston chamber 31, and the first drain oil passage 34 is formed by the outer peripheral surface of the piston 35.
  • the urging force of the spring unit 50 acts on the ball valve body 53, so that the ball valve body 53 is held in the closed position in the accommodation space 44, and the connection hole 45 is closed by the outer peripheral surface of the ball valve body 53.
  • the lubricating oil passage is formed in the engine case, and is configured to increase the supply hydraulic pressure in accordance with an increase in the amount of oil supplied from the engine lubricating oil supply device 1.
  • the lubricating oil discharged from the oil pump 10 is sent to the lubricating oil passage of the engine through the discharge hole 16 and also to the oil amount adjusting valve 20 through the relief hole 21 provided in the path of the discharge hole 16. Sent. At this time, since the urging force of the spring unit 50 is larger than the oil pressure in the piston chamber 31, the connection hole 45 of the switching valve 40 passes through the relief hole 21 in a state where it is closed by the ball valve body 53. The lubricating oil flows into the downstream chamber 33 through the orifice 38 of the piston 35, and the hydraulic pressure in the downstream chamber 33 and the hydraulic pressure in the relief hole 21 (the hydraulic pressure on the front side and the back side of the piston 35) become the same pressure. .
  • the piston 35 continues to be positioned at the closed position on the relief hole 21 side by the urging force of the valve spring 39, and the communication between the relief hole 21 and the first drain oil passage 34 is blocked. For this reason, all the oil discharged from the oil pump 10 is supplied to the engine.
  • the rotational speed of the oil pump 10 is also increased, so that the flow rate of the lubricating oil supplied to the engine is increased and the discharge hydraulic pressure is also increased.
  • the flow rate of the lubricating oil necessary for engine lubrication is not necessarily proportional to the engine speed. Therefore, if the engine speed is increased in this state (the oil pump 10 is increased), the oil pressure of the lubricating oil increases and engine output loss occurs. Therefore, a part of the lubricating oil is drained. Reduce oil pressure.
  • the ball valve body 53 becomes the urging force of the spring unit 50 by this hydraulic pressure.
  • the connecting hole 45 is opened by moving to the right against the lubricating oil in the downstream chamber 33 and flows into the accommodating space 44 in the housing 41 from the connecting hole 45.
  • the inflowing lubricating oil is relieved to the oil pan T from the second drain oil passage 46 formed through the housing 41.
  • the amount of right movement of the piston 35 increases as the pressure difference between the upstream chamber 32 side and the downstream chamber 33 side of the piston 35 increases. A part of the lubricating oil discharged from the oil pump 10 is relieved from the first drain oil passage 34 opened by this pressure difference.
  • the amount of lubricating oil that is relieved from the lubricating oil supplied from the oil pump 10 to the engine is changed in accordance with the pressure of the lubricating oil discharged from the oil pump 10 that rotates in proportion to the rotational speed of the engine. be able to.
  • the flow rate of the lubricating oil supplied to the engine is controlled so that the relationship between the engine speed and the discharge pressure is as shown by the solid line in the graph of FIG.
  • the hydraulic pressure corresponding to the required oil flow rate can be obtained. Therefore, for example, at the rated speed of the engine, the discharge pressure can be reduced by S in FIG. 3 as compared with an oil pump that does not perform the relief of the lubricating oil, so that the output loss of the engine can be reduced. .
  • the work amount of the oil pump 10 also varies depending on the oil temperature of the lubricating oil. For example, when the oil temperature is low such as when the engine is cold started, the viscosity of the lubricating oil increases. Even if they are the same, the work of the oil pump 10 increases. Therefore, if the oil pump 10 is operated more than necessary regardless of the oil temperature of the oil, the oil pump 10 performs extra work, and as a result, the friction becomes high and the engine fuel consumption is reduced. become.
  • the engine lubricating oil supply device 1 uses the change in the spring constant of the shape memory spring 51 according to the sensed temperature to press the ball valve body 53. (Responsibility of the urging force by the two springs 51 and 52) is a mechanism for changing the lubricating oil according to the temperature of the lubricating oil sensed directly or indirectly by the shape memory spring 51.
  • the operating pressure of the oil amount adjusting valve 20 can be changed according to the oil temperature.
  • the shape memory spring 51 changes the spring constant in accordance with the sensed temperature, so the ball valve body 53 is moved to the right against the urging force of the spring unit 50 to open the connecting hole 45. Therefore, the operating pressure (the oil pressure of the lubricating oil) necessary for this also changes according to the detected temperature.
  • FIG. 4 shows the relationship between the oil temperature of the lubricating oil and the operating pressure of the oil amount adjusting valve 20.
  • the transformation temperature of the shape memory spring 51 is 50 ° C.
  • only the biasing force of the bias spring 52 of the spring unit 50 is applied to the ball valve body 53 when the oil temperature of the lubricating oil is less than 50 ° C. (low temperature state). Therefore, the operating pressure for moving the piston 35 to the right is relatively low.
  • the shape memory spring 51 expands and the spring constant increases as the oil temperature rises.
  • the urging forces (combined forces) 51 and 52 also act on the ball valve body 53, and the operating pressure for moving the piston 35 to the right increases with the oil temperature. Furthermore, when the oil temperature of the lubricating oil exceeds 70 ° C., the shape memory spring 51 is maintained in the original memory state, the spring constant becomes substantially constant, and the operating pressure for moving the piston 35 to the right is also kept substantially constant.
  • the amount of oil to be relieved out of the oil discharged from the oil pump 10 is The amount of relief of the lubricating oil is increased when the lubricating oil is in a low temperature state, that is, in a high viscosity state.
  • FIG. 5 shows the relationship between the engine speed, the discharge pressure, and the drive loss when the oil temperature of the lubricating oil is 30 ° C., 60 ° C., and 125 ° C. in the engine lubricating oil supply apparatus 1.
  • the oil temperature is less than the transformation temperature of the shape memory spring 51 as the valve operating pressure changes according to the oil temperature of the lubricating oil described above.
  • the discharge pressure is kept low at 30 ° C., the discharge pressure is high at 60 ° C. exceeding the transformation temperature, and the discharge pressure is further increased at 125 ° C., which is a higher temperature.
  • the excessive amount of work of the oil pump 10 at the low temperature can be achieved by increasing the relief amount of the lubricating oil to keep the discharge pressure small. Can be reduced (reduction in engine output loss). As the oil temperature rises, the relief pressure of the lubricating oil is reduced and the discharge pressure is increased to match the engine requirements in the high output and high rotation range (high engine load) at high oil temperatures. The amount of oil to be fed can be supplied. Further, by reducing the flow rate of oil supplied to the engine when the oil temperature is low, such as when the engine is started, engine warm-up can be promoted and early warm-up can be realized.
  • the operating pressure of the oil amount adjusting valve 20 for opening the drain oil passages 34 and 46 for the lubricating oil may be adjusted based on the balance with the spring urging force of the spring unit 50 that changes by sensing the oil temperature. it can. For this reason, the amount of lubricating oil to be relieved out of the lubricating oil supplied from the oil pump 10 to the engine can be appropriately adjusted according to the rotational speed of the oil pump 10 and the oil temperature of the lubricating oil.
  • the required amount of oil corresponding to the engine speed can be appropriately supplied, and the oil pressure can be reduced by lowering the pump discharge pressure under low temperature conditions where the lubricating oil has a high viscosity, for example, during cold start.
  • the pump 10 does not perform excessive work (without increasing friction), can efficiently use the engine output, and can improve the fuel consumption of the engine.
  • the flow control of the lubricating oil according to the oil temperature is realized by a simple configuration that does not use any electrical control by the controller (ECU).
  • ECU controller
  • the present invention is not limited to this embodiment.
  • the configuration of the external meshing gear pump is exemplified and described as the oil pump.
  • the present invention is not limited to this, and other oil pumps such as an internal meshing gear pump and a trochoid pump may be used. Even if it uses and comprises, the same effect can be acquired.
  • the external meshing gear pump three gears (gears) are arranged in a row in one casing to form two sets of gear pumps, and an oil amount adjusting valve is provided only in the discharge path of one gear pump, The discharge amount of the one gear pump may be adjusted based on the engine speed, the oil temperature and the pressure of the oil.
  • valve body 53 for opening and closing the connection hole 53 is formed in a spherical shape
  • the present invention is not limited to this, and for example, it is formed in a hemispherical shape, a conical shape, or the like. May be.
  • supply means for appropriately supplying a small amount of lubricating oil from the oil pan T to the shape memory spring 51 is provided, or in the lubricating oil in the piston chamber 31 and the discharge hole 16, the discharge pressure varies substantially.
  • the shape memory spring 51 directly senses the oil temperature, thereby operating the valve. The pressure may be adjusted more accurately according to the oil temperature of the lubricating oil.
  • the transformation temperature of the shape memory spring 51 is 50 ° C.
  • the present invention is not limited to this. It is changed and set as appropriate according to the conditions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

L'invention concerne un dispositif (1) d'alimentation en huile lubrifiante pour moteur, dans lequel, en fonction de l'équilibre entre une force de sollicitation d'un ressort (51) à mémoire de forme se modifiant en réponse à la température de l'huile de lubrification et une pression de l'huile lubrifiante pénétrant dans une chambre de piston (31), un trou de connexion est ouvert et fermé par un élément de vanne cylindrique (53). L'huile lubrifiante qui s'écoule du trou de connexion (45) à l'intérieur d'un espace de stockage (44), est drainée par un second passage (46) de drainage, et ainsi, en fonction de l'équilibre entre la force de sollicitation du ressort (39) de soupape et la différence de pression entre une chambre amont (32) et une chambre aval (33) suite à l'écoulement de l'huile lubrifiante à travers un orifice (38), un piston (35) est coulissé et le degré d'ouverture d'un premier passage (34) de drainage est régulé.
PCT/JP2009/006654 2009-12-07 2009-12-07 Dispositif d'alimentation en huile lubrifiante pour moteur WO2011070604A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US13/514,466 US9188031B2 (en) 2009-12-07 2009-12-07 Engine lubricating oil supply device
CN2009801623473A CN102597440A (zh) 2009-12-07 2009-12-07 发动机润滑油供给装置
PCT/JP2009/006654 WO2011070604A1 (fr) 2009-12-07 2009-12-07 Dispositif d'alimentation en huile lubrifiante pour moteur
JP2011544973A JPWO2011070604A1 (ja) 2009-12-07 2009-12-07 エンジン潤滑油供給装置
EP09852004.2A EP2511490A4 (fr) 2009-12-07 2009-12-07 Dispositif d'alimentation en huile lubrifiante pour moteur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/006654 WO2011070604A1 (fr) 2009-12-07 2009-12-07 Dispositif d'alimentation en huile lubrifiante pour moteur

Publications (1)

Publication Number Publication Date
WO2011070604A1 true WO2011070604A1 (fr) 2011-06-16

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US (1) US9188031B2 (fr)
EP (1) EP2511490A4 (fr)
JP (1) JPWO2011070604A1 (fr)
CN (1) CN102597440A (fr)
WO (1) WO2011070604A1 (fr)

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WO2017097605A1 (fr) * 2015-12-07 2017-06-15 Mahle International Gmbh Système d'alimentation en fluide
CN109072732A (zh) * 2016-05-03 2018-12-21 马勒国际有限公司 流体供给系统
JP2019167984A (ja) * 2018-03-22 2019-10-03 いすゞ自動車株式会社 リリーフバルブ
JP2019167986A (ja) * 2018-03-22 2019-10-03 いすゞ自動車株式会社 リリーフバルブ
KR102065258B1 (ko) 2018-07-10 2020-01-10 한국조선해양 주식회사 윤활유펌프 토출유량의 모니터링 방법

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US9494279B2 (en) * 2014-10-21 2016-11-15 Toyota Motor Engineering & Manufacturing North America, Inc. Vehicle oil pan with active noise reduction control
US11168798B2 (en) * 2014-12-22 2021-11-09 Emcara Gas Development Inc. Pressure-balanced valve
GB2536251B (en) * 2015-03-10 2020-09-16 Concentric Birmingham Ltd Recirculation valve
JP6432440B2 (ja) * 2015-05-15 2018-12-05 株式会社デンソー 高圧ポンプ
CN106764369A (zh) * 2015-11-23 2017-05-31 湖南机油泵股份有限公司 一种新型油量可调节式机油泵
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CN106523884B (zh) * 2016-12-20 2018-02-09 湖南机油泵股份有限公司 防卡滞高低压双重保护限压阀及机油泵
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JP2019167984A (ja) * 2018-03-22 2019-10-03 いすゞ自動車株式会社 リリーフバルブ
JP2019167986A (ja) * 2018-03-22 2019-10-03 いすゞ自動車株式会社 リリーフバルブ
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CN102597440A (zh) 2012-07-18
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US9188031B2 (en) 2015-11-17
EP2511490A1 (fr) 2012-10-17
US20120240893A1 (en) 2012-09-27

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