WO2009101907A1 - ラッシュアジャスタ - Google Patents
ラッシュアジャスタ Download PDFInfo
- Publication number
- WO2009101907A1 WO2009101907A1 PCT/JP2009/052072 JP2009052072W WO2009101907A1 WO 2009101907 A1 WO2009101907 A1 WO 2009101907A1 JP 2009052072 W JP2009052072 W JP 2009052072W WO 2009101907 A1 WO2009101907 A1 WO 2009101907A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- pressure chamber
- plunger
- valve body
- high pressure
- 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
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2411—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the valve stem and rocker arm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2416—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device attached to an articulated rocker
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2422—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means or a hydraulic adjusting device located between the push rod and rocker arm
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/245—Hydraulic tappets
- F01L1/25—Hydraulic tappets between cam and valve stem
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/245—Hydraulic tappets
- F01L1/255—Hydraulic tappets between cam and rocker arm
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2301/00—Using particular materials
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2301/00—Using particular materials
- F01L2301/02—Using ceramic materials
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2303/00—Manufacturing of components used in valve arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/01—Absolute values
Definitions
- the present invention relates to a hydraulic lash adjuster.
- Patent Document 1 discloses a hydraulic lash adjuster used in a valve gear.
- the lash adjuster includes a bottomed cylindrical body and a bottomed cylindrical plunger housed in the body so as to be vertically movable, and supports the rocker arm at an upper end portion of the plunger protruding from the body. ing.
- the hollow interior of the plunger is a low pressure chamber
- the lower end space of the body is a high pressure chamber defined by the bottom wall of the plunger
- a valve port of a check valve is opened in the bottom wall of the plunger.
- Hydraulic oil is supplied to the low pressure chamber, and a part of the hydraulic oil in the low pressure chamber fills the high pressure chamber through the valve port.
- a valve body constituting a check valve and a valve spring for urging the valve body toward the valve port (valve closing direction) are accommodated, and in a state where the plunger is stationary, Since the valve body is held at the valve closing position closing the valve port by the biasing of the valve spring, the check valve is closed.
- valve body keeps the valve opening closed when the plunger is lifted.
- the opening degree of the valve port may be insufficient, which may hinder the smooth upward movement of the plunger.
- the present invention has been completed based on the above circumstances, and it is an object of the present invention to avoid a delay in the movement of the valve to the valve closing position when the plunger is lowered.
- the invention according to claim 1 is capable of moving up and down while being in sliding contact with a bottomed cylindrical body and the inner peripheral surface of the body, and biased upward by a return spring.
- the low pressure chamber being provided in the plunger and having the hydraulic fluid stored therein, and the space between the low pressure chamber and the low pressure chamber by the bottom wall of the plunger
- the check valve is disposed in a valve port penetrating the bottom wall of the plunger and in the high pressure chamber and is integral with the plunger Up and down Between the valve opening position spaced apart from the valve port and mounted on the retainer in the high pressure chamber and the valve closing position above the valve opening position and closing the valve port
- Sectional view of the lash adjuster of Embodiment 1 Partially enlarged sectional view showing a state in which the check valve is open Partially enlarged sectional view showing a state in which the check valve is closed
- the first embodiment of the present invention will be described below with reference to FIGS. 1 to 3.
- a valve gear (not shown) of an internal combustion engine to which the hydraulic lash adjuster 10 of the present embodiment is applied will be described.
- the valve gear includes a valve, a lash adjuster 10, a rocker arm, and a cam.
- the rocker arm moves up and down the valve while swinging up and down with the upper end of the lash adjuster 10 as a fulcrum.
- the lash adjuster 10 is configured to include a body 11, a plunger 12 and a check valve 27.
- the body 11 has a bottomed cylindrical shape in which a cylindrical circumferential surface wall 14 is raised from the peripheral edge of a circular bottom surface wall 13 and is in a mounting hole (not shown) opened on the upper surface of a cylinder head (not shown) It is fixed to At a position close to the upper end of the circumferential wall 14 of the body 11, an external communication hole 15 is formed between the inner and outer circumferential surfaces thereof.
- the external communication hole 15 communicates with a hydraulic fluid supply passage (not shown) provided in the cylinder head.
- the plunger 12 has a bottomed cylindrical shape in which a cylindrical peripheral wall 18 is raised from the peripheral edge of the circular bottom wall 17, and is fitted into the body 11 from above, and the upper and lower surfaces are in sliding contact with each other. It is supposed to move.
- the upper end portion of the plunger 12 protrudes upward from the upper end of the body 11, and the upper end portion of the plunger 12 is formed with a substantially hemispherical (dome-like) support portion 19.
- a rocker arm abuts on the outer surface (upper surface) of the support portion 19 from above, and the support portion 19 supports a swing fulcrum of the rocker arm. That is, a downward load from the rocker arm acts on the plunger 12.
- the peripheral wall 18 of the plunger 12 is formed with an internal communication hole 23 in the form of being penetrated from the outer periphery to the inner periphery.
- the inner communication hole 23 and the outer communication hole 15 of the body 11 described above are formed via the communication passage 22 in the circumferential direction formed between the inner periphery of the peripheral wall 14 of the body 11 and the outer periphery of the peripheral wall 18 of the plunger 12. It is in communication with each other.
- a rib 21 is formed in the form of concentrically protruding downward from the outer peripheral edge thereof.
- the hollow interior of the plunger 12 is a low pressure chamber 24. Further, at the hollow lower end portion of the body 11, a high pressure chamber 25 partitioned from the low pressure chamber 24 by the bottom wall 17 of the plunger 12 is formed.
- the check valve 27 allows inflow of hydraulic oil from the low pressure chamber 24 to the high pressure chamber 25 in the open state, and blocks inflow of hydraulic oil from the high pressure chamber 25 to the low pressure chamber 24 in the closed state. It comprises the valve port 28, the retainer 30, and the valve body 29.
- the valve port 28 is formed in the bottom wall 17 of the plunger 12 and is concentrically disposed at the center of the bottom wall 17 so as to penetrate the bottom wall 17 up and down.
- the retainer 30 is made of metal and has a circular base portion 32 concentric with the valve port 28, a cylindrical cylindrical portion 33 extending upward from the outer peripheral edge of the base portion 32, and a cylindrical portion 33. And a spring receiving portion 34 extending from the upper end edge to the outer peripheral side so as to be folded back in a substantially semicircular shape concentrically and configured to have a bottomed cylindrical shape as a whole.
- the diameter of the base portion 32 is larger than the diameter of the valve body 29, and the upper surface of the base portion 32 is concentrically raised on the central portion of the base portion 32 (that is, the area where the valve body 29 at the valve open position is mounted)
- a thick portion 35 is formed.
- the diameter of the thick portion 35 is a size slightly smaller than the diameter of the valve body 29 described later.
- the cylindrical portion 33 is configured to surround the valve body 29 housed in the retainer 30. Furthermore, in the cylindrical portion 33, a plurality of openings 36 penetrating from the inner circumferential surface to the outer circumferential surface are formed at equal angular intervals in the circumferential direction.
- the retainer 30 is disposed in the high pressure chamber 25 and attached to the plunger 12 in a state where the spring receiving portion 34 is fitted to the inner periphery of the rib 21 and in contact with the lower surface of the bottom wall 17. Further, in the high pressure chamber 25, a return spring 26 formed of a compression coil spring coaxial with the valve port 28 is accommodated. The coil diameter of the return spring 26 is smaller than the inner diameter of the rib 21 and larger than the outer diameter of the cylindrical portion 33 of the retainer 30. The return spring 26 has its lower end portion in contact with the bottom surface of the high pressure chamber 25 (the upper surface of the bottom wall 13) and its upper end portion in contact with the concave lower surface of the spring receiving portion 34.
- the valve body 29 is formed of a steel (SUJ2) ball and is disposed in the high pressure chamber 25.
- the valve body 29 is opened and opened within a range between the bottom wall 17 and the thick portion 35 (substrate portion 32) in the cylindrical portion 33 of the retainer 30 (see FIG. 2). It is provided so as to be able to move up and down by a small size between a closed position above the position (see FIG. 3).
- the valve opening position is a position at which the valve body 29 is placed on the upper surface of the thick portion 35, and the valve closing position is such that the valve body 29 abuts against the seat surface 31 in a fluid tight manner. It is a position to close.
- the upper end portion of the valve body 29 is kept surrounded by the seat surface 31 regardless of the position between the valve opening position and the valve closing position.
- the distance between the valve body 29 and the seat surface 31 in the horizontal direction is The maximum value is obtained, but since the interval at this time is small, there is no possibility that the valve body 29 is largely shaken in the horizontal direction or largely separated from the valve port 28. That is, the seat surface 31 exhibits the function of guiding the valve body 29.
- the inner diameter A of the valve port 28 is 2 to 2.2 mm
- the diameter B of the valve body 29 is 3 mm, which is larger than the inner diameter of the valve port 28.
- the vertical movement stroke C between the valve opening position and the valve closing position of the valve body 29 is 0.05 to 0.2 mm.
- the diameter D of the contact area (contact circle) between the valve body 29 and the seat surface 31 when the valve body 29 is in the valve closed position is 2.38 mm.
- the minimum distance E between the valve body 29 and the seat surface 31 when the valve body 29 is in the open position is 0.05 to 0.2 mm.
- the specific gravity of the valve body 29 is 7.8.
- the hydraulic oil supplied from the hydraulic oil supply passage of the cylinder head to the lash adjuster 10 is stored in the low pressure chamber 24 sequentially through the outer communication hole 15, the communication passage 22 and the inner communication hole 23.
- the high pressure chamber 25 is filled through the valve port 28.
- the valve body 29 Since the upper end portion of the valve body 29 is surrounded by the seat surface 31 when the valve body 29 ascends, the valve body 29 is in the horizontal direction (perpendicular to the moving direction between the valve opening position and the valve closing position).
- the seat surface 31 can be reliably abutted without being largely misaligned in the direction. Further, since the seat surface 31 has a form in which the diameter decreases toward the valve port 28, the valve body 29 is guided by the seat surface 31 so as to approach the valve port 28. Therefore, the valve body 29 can reliably close the valve port 28 (reach the valve closed position). Furthermore, since the tubular portion 33 is surrounded inside the retainer 30, the positional displacement of the valve body 29 in the horizontal direction is also prevented by the presence of the tubular portion 33.
- the time required for the check valve 27 to switch to the closed state after the plunger 12 starts to descend is very short. After the check valve 27 is closed, the hydraulic oil in the high pressure chamber 25 passes through a slight gap between the outer peripheral surface of the plunger 12 and the inner peripheral surface of the body 11 as the plunger 12 descends. Flows out and flows into the low pressure chamber 24 from the internal communication hole 23.
- valve body 29 does not go down excessively through the predetermined valve opening position. Therefore, when the plunger 12 turns from rising to lowering, the valve body 29 can quickly reach the valve closing position without delaying the return operation of the valve body 29 to the valve closing position. Further, since the thick portion 35 in contact with the valve body 29 displaced to the valve opening position has high rigidity, deformation does not easily occur even if the valve body 29 abuts (collision).
- the check valve 27 of the lash adjuster 10 includes the valve port 28 penetrating the bottom wall 17 of the plunger 12 and the retainer disposed in the high pressure chamber 25 and vertically moving integrally with the plunger 12. 30 and a valve body 29 capable of moving up and down between the valve opening position and the valve closing position in the high pressure chamber 25.
- the valve body 29 is a retainer by its own weight. It is placed at 30 and held at the valve opening position.
- valve spring for urging the valve body 29 toward the valve closing position, and to increase the biasing force of the valve spring.
- the valve body 29 may keep the valve port 28 closed when the plunger 12 is lifted, or the opening degree of the valve port 28 may be insufficient, which may hinder smooth upward movement of the plunger 12.
- the valve spring since the valve spring is not used, there is no possibility that the lifting operation of the plunger 12 will be hindered due to the use of the valve spring.
- the following effects can be expected by using a structure that does not use a valve spring that biases the valve body 29 toward the valve closing position. That is, in a state where the cam base circle of the cam presses the rocker arm and the plunger 12 is at rest, the check valve 27 is kept open to allow the flow of hydraulic oil at the valve port 28, If the load applied from the rocker arm to the plunger 12 slightly fluctuates due to the dimensional tolerance of the cam base circle, the sudden temperature change of the valve gear, etc., the check valve 27 is kept open. Vertical movement of the plunger 12 is allowed. Thereby, it is possible to reduce the load on the valve, the rocker arm, the cam, the plunger 12, etc. and to avoid the stress concentration.
- the valve body is made of steel (SUJ2), but according to the present invention, the valve body may be made of metal other than steel, and includes silicon nitride having a smaller specific gravity than metal. It may be made of ceramics.
- the diameter of the valve body is 3 mm, but according to the present invention, the diameter of the valve body may be smaller than 3 mm or larger than 3 mm.
- the vertical movement stroke between the valve opening position and the valve closing position of the valve body is 0.05 to 0.2 mm, but according to the present invention, the vertical movement stroke of the valve body is , May be smaller than 0.05 mm, and may be larger than 0.2 mm.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
プランジャが上昇する際には、弁体がその自重により開弁位置に保持されたままの状態で、低圧室内の作動油が弁口を通って高圧室内に流入する。このとき、プランジャの上昇速度が高速であっても、弁体はリテーナに載置された状態に保たれるので、弁体と弁口との距離が大きくなることはない。したがって、その後にプランジャが下降を開始したときには、弁体が速やかに閉弁位置へ移動して弁口を閉塞する。
11…ボディ
12…プランジャ
17…底壁
24…低圧室
25…高圧室
26…リターンスプリング
27…逆止弁
28…弁口
29…弁体
30…リテーナ
以下、本発明を具体化した実施形態1を図1~図3を参照して説明する。本実施形態の油圧式のラッシュアジャスタ10が適用される内燃機関の動弁装置(図示せず)について説明すると、動弁装置は、バルブ、ラッシュアジャスタ10、ロッカアーム、及びカムを備えて構成され、カムの回転に伴い、ロッカアームがラッシュアジャスタ10の上端を支点として上下方向に揺動しつつバルブを上下動させるようになっている周知の構造のものである。
ボディ11は、円形の底面壁13の周縁から円筒状の周面壁14を立ち上げた有底筒状をなし、シリンダヘッド(図示せず)の上面に開口させた取付孔(図示せず)内に固定されている。ボディ11の周面壁14における上端に近い位置には、その内外両周面間に貫通する外部連通孔15が形成されている。この外部連通孔15は、シリンダヘッド内に設けた作動油供給路(図示せず)に連通している。
弁口28は、プランジャ12の底壁17に形成され、底壁17の中心に同心に配置されていて底壁17を上下に貫通する形態である。弁口28における下側(高圧室25側)の開口縁には、下広がり(高圧室25側に向かって拡径するような形態)であって断面が略四半円弧状をなすシート面31が形成されている。
プランジャ12が上下動せずに静止している状態では、図2に示すように、弁体29は、その自重により、リテーナ30の厚肉部35の上面に載置された開弁位置にあり、逆止弁27は開弁状態に保たれている。
本発明は上記記述及び図面によって説明した実施形態に限定されるものではなく、例えば次のような実施態様も本発明の技術的範囲に含まれる。
(1)上記実施形態では弁体を鋼製(SUJ2)としたが、本発明によれば、弁体を、鋼以外の金属製であってもよく、金属よりも比重の小さい窒化ケイ素を含むセラミックス製であってもよい。
(2)上記実施形態では弁体の直径を3mmとしたが、本発明によれば、弁体の直径は、3mmより小さくてもよく、3mmより大きくてもよい。
(3)上記実施形態では、弁体の開弁位置と閉弁位置との間の上下動ストロークを0.05~0.2mmとしたが、本発明によれば、弁体の上下動ストロークは、0.05mmより小さくてもよく、0.2mmより大きくてもよい。
Claims (5)
- 有底筒状のボディと、
前記ボディの内周面に摺接しつつ上下移動可能であって、リターンスプリングによって上方へ付勢された有底筒状のプランジャと、
前記プランジャ内に設けられて作動油が貯留される低圧室と、
前記ボディの中空内下端部に形成され、前記プランジャの底壁によって前記低圧室との間を仕切られるとともに前記作動油が充填される高圧室と、
開弁状態では前記低圧室から前記高圧室への前記作動油の流入を許容し、閉弁状態では前記高圧室から前記低圧室への前記作動油の流入を遮断する逆止弁とを備えたラッシュアジャスタにおいて、
前記逆止弁は、
前記プランジャの前記底壁を貫通する弁口と、
前記高圧室内に配されて前記プランジャと一体的に上下動するリテーナと、
前記高圧室内において、前記弁口から離間して前記リテーナに載置される開弁位置と、前記開弁位置よりも上方であって前記弁口を閉塞する閉弁位置との間で上下移動可能な弁体とを備えており、
前記プランジャが静止している状態では、前記弁体がその自重により前記開弁位置に保持されるようになっていることを特徴とするラッシュアジャスタ。 - 前記弁口における前記高圧室側の開口縁には、前記高圧室側に向かって拡径する形態のシート面が形成されていることを特徴とする請求項1記載のラッシュアジャスタ。
- 前記弁体が開弁位置と閉弁位置との間のいずれの位置にあっても、前記弁体の上端部は前記シート面によって囲まれた状態に保たれていることを特徴とする請求項2記載のラッシュアジャスタ。
- 前記リテーナは、
開弁位置にある前記弁体を載置させる基板部と、
前記基板部の外周縁から上方へ延出した形態であって前記弁体を包囲する形態の筒状部とを備えて構成されていることを特徴とする請求項1記載のラッシュアジャスタ。 - 前記基板部のうち開弁位置にある前記弁体が載置する領域には、部分的に盛り上げた形態の厚肉部が形成されていることを特徴とする請求項4記載のラッシュアジャスタ。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP09709467.6A EP2256308B1 (en) | 2008-02-13 | 2009-02-06 | Lash adjuster |
US12/865,967 US8371258B2 (en) | 2008-02-13 | 2009-02-06 | Lash adjuster |
CN2009801035611A CN101932798A (zh) | 2008-02-13 | 2009-02-06 | 气门间隙调节器 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008032059A JP2009191690A (ja) | 2008-02-13 | 2008-02-13 | ラッシュアジャスタ |
JP2008-032059 | 2008-02-13 |
Publications (1)
Publication Number | Publication Date |
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WO2009101907A1 true WO2009101907A1 (ja) | 2009-08-20 |
Family
ID=40956938
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2009/052072 WO2009101907A1 (ja) | 2008-02-13 | 2009-02-06 | ラッシュアジャスタ |
Country Status (6)
Country | Link |
---|---|
US (1) | US8371258B2 (ja) |
EP (1) | EP2256308B1 (ja) |
JP (1) | JP2009191690A (ja) |
KR (1) | KR101570889B1 (ja) |
CN (1) | CN101932798A (ja) |
WO (1) | WO2009101907A1 (ja) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
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JP5456567B2 (ja) * | 2010-05-12 | 2014-04-02 | 株式会社オティックス | ラッシュアジャスタ |
WO2012071265A2 (en) * | 2010-11-22 | 2012-05-31 | Jacobs Vehicle Systems, Inc. | Appartus and method for valve lash adjustment |
JP2014156782A (ja) * | 2013-02-14 | 2014-08-28 | Otics Corp | ラッシュアジャスタ |
CN103939164B (zh) * | 2014-04-25 | 2016-08-17 | 安徽江淮汽车股份有限公司 | 一种发动机气门间隙调节器 |
DE102014215422A1 (de) * | 2014-08-05 | 2016-02-11 | Schaeffler Technologies AG & Co. KG | Hydraulische Spielausgleichsvorrichtung für einen Ventiltrieb einer Brennkraftmaschine |
EP3015122B1 (en) | 2014-11-03 | 2017-05-10 | B. Braun Avitum AG | Attachment assembly for attaching a fluid bag to a fluid warmer of a system for extracorporeal blood treatment |
JP6599735B2 (ja) | 2015-11-20 | 2019-10-30 | 株式会社オティックス | ラッシュアジャスタ |
DE102019113959A1 (de) * | 2019-05-24 | 2020-11-26 | Schaeffler Technologies AG & Co. KG | In einer Aufnahme eines Zylinderkopfes einer Brennkraftmaschine sitzendes, druckölanschlussfreies, hydraulischen Abstützelement |
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JPH0716004Y2 (ja) * | 1988-09-24 | 1995-04-12 | 三菱自動車工業株式会社 | 多気筒エンジンのシリンダヘッド |
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- 2008-02-13 JP JP2008032059A patent/JP2009191690A/ja active Pending
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- 2009-02-06 WO PCT/JP2009/052072 patent/WO2009101907A1/ja active Application Filing
- 2009-02-06 CN CN2009801035611A patent/CN101932798A/zh active Pending
- 2009-02-06 US US12/865,967 patent/US8371258B2/en not_active Expired - Fee Related
- 2009-02-06 KR KR1020107013530A patent/KR101570889B1/ko active IP Right Grant
- 2009-02-06 EP EP09709467.6A patent/EP2256308B1/en not_active Not-in-force
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JPS58178812A (ja) * | 1982-04-14 | 1983-10-19 | Honda Motor Co Ltd | 油圧式ラツシユアジヤスタ |
JPH05288020A (ja) | 1992-04-09 | 1993-11-02 | Nippon Seiko Kk | 内燃機関のラッシュアジャスタ |
JPH09324609A (ja) * | 1996-03-08 | 1997-12-16 | Eaton Corp | 液圧ラッシュアジャスタ |
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Also Published As
Publication number | Publication date |
---|---|
US8371258B2 (en) | 2013-02-12 |
US20110000452A1 (en) | 2011-01-06 |
KR101570889B1 (ko) | 2015-11-20 |
EP2256308B1 (en) | 2016-04-13 |
EP2256308A1 (en) | 2010-12-01 |
KR20100120635A (ko) | 2010-11-16 |
CN101932798A (zh) | 2010-12-29 |
EP2256308A4 (en) | 2011-06-08 |
JP2009191690A (ja) | 2009-08-27 |
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