WO2009119362A1 - ラッシュアジャスタ - Google Patents
ラッシュアジャスタ Download PDFInfo
- Publication number
- WO2009119362A1 WO2009119362A1 PCT/JP2009/055002 JP2009055002W WO2009119362A1 WO 2009119362 A1 WO2009119362 A1 WO 2009119362A1 JP 2009055002 W JP2009055002 W JP 2009055002W WO 2009119362 A1 WO2009119362 A1 WO 2009119362A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- case
- lash adjuster
- adjuster according
- protrusion
- hole
- Prior art date
Links
Images
Classifications
-
- 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
-
- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/185—Overhead end-pivot rocking arms
Definitions
- This invention relates to a lash adjuster incorporated in an engine valve gear.
- valve operating device that operates a valve provided at the intake port or exhaust port of an engine
- the central part of the arm supported so as to be swingable with one end as a fulcrum is pushed down by a cam, and the valve stem is moved at the other end of the arm. What is pushed down is known.
- a gap between constituent members of the valve operating device changes due to a difference in thermal expansion generated between the constituent members of the valve operating device during operation of the engine, and abnormal noise and compression leakage may occur due to the change in the clearance. There is. Further, even if the sliding portion of the valve operating device is worn, the gap between the constituent members of the valve operating device changes, and there is a possibility that abnormal noise or compression leakage may occur due to the change in the gap.
- a lash adjuster is incorporated in the valve operating device, and the lash adjuster often absorbs the change in the gap between the components of the valve operating device.
- a lash adjuster As such a lash adjuster, a cylindrical case with a bottom that is inserted into a receiving hole opened on the upper surface of the cylinder head, and an adjustment screw having a male screw on its outer periphery that engages with a female screw formed on the inner periphery of the case. And a return spring that urges the adjusting screw in a direction protruding upward from the case, and supports the arm of the valve gear so as to be swingable at the protruding end of the adjusting screw from the case.
- Patent Documents 1 and 2 Patent Documents 1 and 2
- Patent Document 1 a compression coil spring that applies an axial force in a direction protruding from the case to the adjustment screw is used as the return spring. Moreover, in patent document 2, the torsion spring which provides the adjusting screw with the rotational force of the direction which protrudes from a case is used as a return spring.
- the adjusting screw moves in the axial direction while rotating inside the case according to the change in position, and the valve operating device Absorbs changes in gaps between components.
- JP 2005-273510 A Japanese Utility Model Publication No. 64-34407
- the lash adjuster may rotate the case relative to the accommodation hole due to the force acting between the adjustment screw and the screw surface of the case when a load in the pushing direction is applied to the adjustment screw by the rotation of the cam. there were.
- the case rotates there is a problem that the adjustment screw moves in the pushing direction and the valve lift amount becomes small. Further, the inner surface of the accommodation hole may be worn by the rotation of the case.
- the problem to be solved by the present invention is to prevent the case from rotating when a load in the pushing direction is applied to the adjustment screw.
- a detent means for preventing the case from rotating is provided.
- the anti-rotation means can be constituted by, for example, an anti-rotation protrusion provided on the bottom of the case, and a fitting opening that is fitted to the anti-rotation protrusion and formed on the inner bottom surface of the accommodation hole.
- the case is prevented from rotating by fitting the rotation preventing projection and the fitting port, and therefore the case does not rotate when a force in the pushing direction is applied to the adjustment screw.
- a protrusion having a D-cut portion on the outer periphery a protrusion having a two-chamfered portion on the outer periphery, a regular polygonal columnar protrusion, or a protrusion eccentric with respect to the axial center of the case may be employed as the anti-rotation protrusion. it can.
- the fitting port for example, one end of an air vent hole communicating from the inner bottom surface of the housing hole to the outside can be adopted.
- the lash adjuster when the lash adjuster is inserted into the accommodation hole, air between the bottom of the case and the inner bottom surface of the accommodation hole is discharged through the air vent hole, and the inside of the accommodation hole is maintained at atmospheric pressure. , No reaction force is generated at the bottom of the case, and the assembly workability to the cylinder head is good.
- one end of the air vent hole is used as the fitting port, it is not necessary to form the fitting port separately from the air vent hole, and the cylinder head can be easily formed.
- a through-hole penetrating the bottom of the case vertically can be provided, and the lower end of the through-hole can be opened at the tip of the anti-rotation protrusion. If it does in this way, the engine oil which flowed in in the case through between the external screw of the adjustment screw and the internal screw of the case will be discharged through the through hole and the air vent hole in order. Therefore, suits and contaminants mixed in the engine oil are less likely to stay between the male screw of the adjusting screw and the female screw of the case, and the male screw and the female screw are less likely to wear.
- the anti-rotation means can be constituted by a friction ensuring means for ensuring frictional resistance between the bottom of the case and the inner surface of the receiving hole to prevent the case from rotating.
- an oil film exclusion groove formed on the outer bottom surface of the case can be employed. If it does in this way, the engine oil between the outer bottom face of a case and the inner bottom face of an accommodation hole will escape in an oil film exclusion groove
- the friction ensuring means a satin formed on the outer bottom surface of the case.
- the satin finish may be formed by electric discharge machining or laser processing, but if formed by shot peening, the outer bottom face of the case can be cured to increase wear resistance. .
- the friction ensuring means includes a tapered outer peripheral surface formed in the bottom portion of the case and having a diameter reduced downward, and a tapered inner peripheral surface formed in the housing hole and having a diameter reduced in the downward direction.
- the surface can be fitted to the tapered inner peripheral surface. In this way, a high surface pressure due to the wedge action acts between the tapered outer peripheral surface and the tapered inner peripheral surface, so that a frictional resistance between the tapered outer peripheral surface and the tapered inner peripheral surface can be ensured.
- a recess provided by leaving the peripheral edge on the outer bottom surface of the case can be adopted.
- the outer bottom surface of the case is in contact with the inner bottom surface of the housing hole only at the periphery thereof, and the frictional resistance generated between the outer bottom surface of the case and the inner bottom surface of the housing hole is concentrated on the outer diameter side. The frictional resistance necessary to prevent the case from rotating can be ensured.
- a recess provided on the inner bottom surface of the accommodation hole leaving its peripheral edge may be adopted.
- the friction ensuring means a small-diameter inner peripheral surface formed in the accommodation hole is adopted, and the bottom portion of the case can be press-fitted into the small-diameter inner peripheral surface. In this way, since a high surface pressure is applied by press-fitting between the bottom of the case and the small-diameter inner peripheral surface of the accommodation hole, it is possible to ensure the frictional resistance between the bottom of the case and the inner surface of the accommodation hole. it can.
- the friction ensuring means a rubber or elastomer sheet sandwiched between the outer bottom surface of the case and the inner bottom surface of the accommodation hole can be employed. This prevents the case from rotating because the frictional resistance between the outer bottom surface of the case and the inner bottom surface of the housing hole is higher than when the outer bottom surface of the case and the inner bottom surface of the housing hole are in direct contact with each other. Therefore, the necessary frictional resistance can be ensured.
- an iron pedestal that constitutes the inner bottom surface of the accommodation hole can be adopted as the friction ensuring means.
- the friction coefficient of the inner bottom surface of the receiving hole can be prevented from decreasing with time. The frictional resistance between the bottom of the housing and the inner surface of the receiving hole can be ensured.
- the friction ensuring means a bottomed cylindrical iron sleeve constituting the accommodation hole can be adopted. In this way, since the inner surface of the receiving hole is not easily worn, even when the cylinder head is made of aluminum, it is possible to prevent the friction coefficient of the inner surface of the receiving hole from decreasing with time. And a frictional resistance between the inner surface of the accommodation hole can be ensured.
- the present invention can be applied to a lash adjuster that uses a compression coil spring that applies an axial force in a direction protruding from the case to the adjustment screw as the return spring, and the rotational force in the direction protruding from the case is adjusted.
- the present invention can also be applied to a lash adjuster that uses a torsion spring applied to a screw as the return spring.
- the torsion spring include a torsion coil spring, a spring, and a bamboo spring.
- the male screw and female screw may be triangular, trapezoidal, or sawtooth screws.
- the lash adjuster of the present invention is provided with a detent means for preventing the case from rotating, the case is difficult to rotate when a load in the pushing direction is applied to the adjustment screw. Therefore, the valve lift amount can be prevented from decreasing due to the rotation of the case, and stable performance can be exhibited. In addition, wear on the inner surface of the accommodation hole can be prevented.
- FIG. 2 is an enlarged cross-sectional view showing another example of the anti-rotation protrusion shown in FIG. Sectional view along line VV in FIG.
- FIG. 2 is an enlarged cross-sectional view showing still another example of the anti-rotation protrusion shown in FIG. Sectional view along line VII-VII in FIG.
- FIG. 2 is an enlarged cross-sectional view showing still another example of the anti-rotation protrusion shown in FIG. Sectional view along line IX-IX in FIG.
- FIG. 10 is an enlarged sectional view showing another example of the return spring shown in FIG.
- FIG. 10 is an enlarged sectional view showing still another example of the return spring shown in FIG. Sectional view along line XIII-XIII in FIG.
- FIG. 10 is an enlarged sectional view showing still another example of the return spring shown in FIG.
- FIG. 15 is an enlarged sectional view showing another example of the friction securing means shown in FIG.
- FIG. 15 is an enlarged sectional view showing still another example of the friction ensuring means shown in FIG. FIG.
- FIG. 15 is an enlarged sectional view showing still another example of the friction ensuring means shown in FIG.
- FIG. 15 is an enlarged sectional view showing still another example of the friction ensuring means shown in FIG.
- FIG. 15 is an enlarged sectional view showing still another example of the friction ensuring means shown in FIG.
- FIG. 15 is an enlarged sectional view showing still another example of the friction ensuring means shown in FIG.
- FIG. 15 is an enlarged sectional view showing still another example of the friction ensuring means shown in FIG.
- FIG. 1 shows a valve gear incorporating a lash adjuster 1 according to the first embodiment of the present invention.
- This valve operating apparatus is accommodated in a valve 4 provided in an intake port 3 of the cylinder head 2 of the engine, a valve stem 5 connected to the valve 4, and an accommodation hole 6 opened on the upper surface of the cylinder head 2. It has a lash adjuster 1 and an arm 7 supported so as to be swingable with the lash adjuster 1 as a fulcrum.
- the valve stem 5 extends upward from the valve 4 and slidably penetrates the cylinder head 2.
- An annular spring retainer 8 is fixed to the upper outer periphery of the valve stem 5, and a valve spring 9 is incorporated between the lower surface of the spring retainer 8 and the upper surface of the cylinder head 2.
- the valve spring 9 urges the valve stem 5 upward via the spring retainer 8, and the valve 4 is seated on the valve seat 10 by the urging force.
- the arm 7 has one end supported by the lash adjuster 1 and the other end in contact with the upper end of the valve stem 5.
- a roller 11 is attached to the center of the arm 7, and the roller 11 is in contact with a cam 12 provided above the arm 7.
- the lash adjuster 1 has a bottomed cylindrical case 13 inserted into the receiving hole 6 and a male screw 15 that engages with a female screw 14 formed on the inner periphery of the case 13 on the outer periphery of the lower portion. And an adjustment screw 16 and a return spring 18 incorporated between the adjustment screw 16 and the bottom portion 17 of the case 13.
- the male screw 15 and the female screw 14 are formed in a sawtooth shape in which the flank angle of the pressure side flank 19 that receives pressure when a load in the direction of pushing the adjusting screw 16 into the case 13 is applied is larger than the flank angle of the play side flank 20. Has been.
- the return spring 18 is a compression coil spring.
- the return spring 18 has a lower end supported by the bottom portion 17 of the case 13 and an upper end that applies an axial force in a direction protruding from the case 13 via the spring seat 21 to the adjusting screw 16.
- the adjusting screw 16 is urged by the axial force in a direction protruding upward from the case 13.
- the adjustment screw 16 has a protruding end 22 from the case 13 fitted into a recess 23 formed on the lower surface of the end of the arm 7, and the arm 7 is swung around the protruding end 22. I support it as possible.
- the cylinder head 2 is formed with an air vent hole 25 communicating with the outside from the inner bottom surface 24 of the housing hole 6, and when the lash adjuster 1 is inserted into the housing hole 6, the case 13 and the inner bottom surface of the housing hole 6 are formed. 24 is discharged through the air vent hole 25.
- the bottom portion 17 of the case 13 is formed with a rotation-preventing protrusion 27 that fits into the fitting port 26 formed in the inner bottom surface 24 of the accommodation hole 6.
- the fitting port 26 is one end of the air vent hole 25.
- the anti-rotation protrusion 27 has a D-cut portion 28 on the outer periphery, and the D-cut portion 28 engages with a D-cut portion 29 formed on the inner periphery of the fitting port 26.
- the case 13 is prevented from rotating.
- the D-cut portion 28 is a portion having a shape obtained by cutting the outer periphery along a plane parallel to the plane including the axis of the case 13.
- the case 13 is made of iron in order to ensure the strength of the female screw 14.
- the fitting port 26 having the D-cut portion 29 on the inner periphery and the air vent hole 25 having the fitting port 26 at one end can be formed by aluminum die casting of the cylinder head 2.
- a through-hole 30 penetrating vertically is formed in the bottom portion 17 of the case 13, and a lower end of the through-hole 30 is opened at a tip of the anti-rotation protrusion 27. Therefore, the engine oil that has flowed into the case 13 from the upper end surface of the case 13 through the gap between the male screw 15 and the female screw 14 passes through the through hole 30 and the air vent hole 25 in order and is discharged from the case 13.
- the biasing force of the valve spring 9 acts on the adjustment screw 16 even when the base circle 12b of the cam 12 is at the position of the roller 11.
- the amount of protrusion of the adjusting screw 16 when the cam 12 rotates and the load in the pushing direction is released is smaller than the amount of pushing of the adjusting screw 16 when the cam crest 12a of the cam 12 pushes down the arm 7.
- the adjustment screw 16 gradually moves in the pushing direction and the valve stem 5 rises, so that no gap is generated between the contact surfaces of the valve 4 and the valve seat 10.
- the case 13 is prevented from rotating by the fitting of the rotation preventing projection 27 and the fitting port 26, so that the case 13 does not rotate when a load in the pushing direction is applied to the adjusting screw 16. Therefore, it is possible to prevent a decrease in the valve lift amount due to the rotation of the case 13 and to exhibit stable performance. Further, the inner surface of the accommodation hole 6 is not worn.
- the air between the bottom portion 17 of the case 13 and the inner bottom surface 24 of the accommodation hole 6 is discharged through the air vent hole 25, Since the inside of the accommodation hole 6 is maintained at atmospheric pressure, no reaction force is generated at the bottom portion 17 of the case 13, and the assembly workability to the cylinder head 2 is good. Further, since one end of the air vent hole 25 is used as the fitting port 26, it is not necessary to form the fitting port 26 separately from the air vent hole 25, and the cylinder head 2 can be easily formed.
- the engine oil that has flowed into the case 13 through the space between the male screw 15 of the adjusting screw 16 and the female screw 14 of the case 13 is discharged through the through hole 30 and the air vent hole 25 in order. Therefore, suits and contaminants mixed in the engine oil are unlikely to stay between the male screw 15 of the adjusting screw 16 and the female screw 14 of the case 13, and the male screw 15 and the female screw 14 are not easily worn.
- the anti-rotation projection 27 provided on the bottom portion 17 of the case 13 has been described as an example of the anti-rotation projection 27 having the D-cut portion 28 on the outer periphery, but instead of the anti-rotation projection 27, FIG.
- the anti-rotation protrusion 32 having the two chamfered portions 31, 31 is adopted on the outer periphery, and the two chamfered portions 31, 31 are formed on the inner periphery of the fitting port 33.
- the case 13 may be prevented from rotating by engaging with.
- the two chamfered portions 31, 31 are portions having a shape obtained by cutting the outer periphery along two planes parallel to the plane including the axis of the case 13.
- a rotation preventing projection 35 having a regular polygonal column shape (for example, a regular hexagonal column) is adopted, and the rotation preventing projection 35 is formed in a regular polygonal column shape.
- the case 13 may be prevented from rotating by being fitted into the fitting port 36.
- the workability of assembling the lash adjuster 1 to the cylinder head 2 is further improved.
- an anti-rotation protrusion 37 that is eccentric with respect to the axial center of the case 13 is adopted, and the anti-rotation protrusion 37 is used as the axis of the housing hole 6.
- the case 13 may be prevented from rotating by being fitted into a fitting port 38 that is eccentric with respect to the center.
- FIG. 10 shows a lash adjuster 41 according to the second embodiment of the present invention.
- the lash adjuster 41 uses a non-rotating projection 27 having a D-cut portion 28 on the outer periphery as the non-rotating projection 27 of the bottom 17 of the case 13.
- portions corresponding to the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
- the adjusting screw 16 supports a pivot member 16A inserted in the case 13 so as to be slidable in the axial direction, a male screw member 16B supporting the insertion end of the pivot member 16A into the case 13 and having a male screw 15 on the outer periphery, and a pivot.
- the disc spring 16C is sandwiched between the member 16A and the male screw member 16B.
- the return spring 18 is a torsion coil spring.
- the return spring 18 has a lower end locked in a locking hole 42 formed in the bottom portion 17 of the case 13, and an upper end locked in a locking hole 43 formed in the male screw member 16B.
- a detent protrusion 27 having a D-cut portion 28 is formed on the outer periphery of the bottom portion 17 of the case 13, and the detent protrusion 27 is fitted in the fitting port 26 of the inner bottom surface 24 of the accommodation hole 6. .
- the case 13 is prevented from rotating by the fitting of the rotation preventing projection 27 and the fitting port 26, so that it is possible to prevent the valve lift amount from decreasing due to the rotation of the case 13. And can exhibit stable performance.
- the lash adjuster 41 is provided between the male screw member 16B and the pivot member 16A when the engine is stopped in a high temperature state, and thereafter, when the engine is cooled and a contraction difference is generated between the constituent members of the valve gear.
- the disc spring 16C is compressed, the contraction difference is absorbed. Therefore, when the engine is restarted, a gap due to a contraction difference between the constituent members of the valve operating device does not occur between the valve 4 and the valve seat 10, and compression leakage does not occur.
- the return spring 18 may be a cylinder wound as shown in FIG. 10 or a cone wound as shown in FIG. 11. May be.
- the return spring 18 may employ a torsion spring other than the torsion coil spring.
- the return spring 18 is a bamboo child spring in which a thin plate material is wound spirally.
- the return spring 18 has a large-diameter end that is prevented from rotating around the bottom 17 of the case 13, and a small-diameter end that is inserted into a slit formed in the projection 44 at the insertion end of the male screw member 16 ⁇ / b> B into the case 13.
- the rotational force in the direction in which the pivot member 16A protrudes from the case 13 is applied to the male screw member 16B.
- the male screw 15 on the outer periphery of the male screw member 16B and the female screw 14 on the inner periphery of the case 13 are vertically symmetrical trapezoidal screws.
- the return spring 18 is a spring spring in which a thin plate material is wound in a spiral shape.
- the return spring 18 has a large-diameter end that is prevented from rotating around the bottom 17 of the case 13, and a small-diameter end that is inserted into a slit formed in the protrusion 45 at the insertion end of the male screw member 16 ⁇ / b> B into the case 13.
- the rotational force in the direction in which the pivot member 16A protrudes from the case 13 is applied to the male screw member 16B.
- the external thread 15 on the outer periphery of the external thread member 16B and the internal thread 14 on the inner periphery of the case 13 are vertically symmetrical triangular screws.
- the bottom portion 17 of the case 13 may be formed integrally with the case 13 as shown in the figure, but the bottom portion 17 is formed separately from the case 13 and the bottom portion 17 is formed at the lower end of the case 13. It may be fixed to.
- 15 and 16 show a lash adjuster 51 according to a third embodiment of the present invention.
- the outer bottom surface 52 of the case 13 is in contact with the inner bottom surface 24 of the accommodation hole 6 so that when the case 13 is loaded with an axial load, the axial load is received by the inner bottom surface 24 of the accommodation hole 6. It has become.
- the outer bottom surface 52 of the case 13 is formed with a plurality of oil film removal grooves 53 extending linearly.
- the lash adjuster 51 generates a rotational force between the pressure-side flanks 19 and 19 of the male screw 15 and the female screw 14 when a load in the pushing direction is applied to the adjusting screw 16, but the outer bottom surface 52 of the case 13 and the receiving hole The rotation of the case 13 is prevented by the frictional resistance between the inner bottom surface 24 and the inner bottom surface 24.
- the oil film exclusion groove 53 is formed on the outer bottom surface 52 of the case 13, but as shown in FIG. A satin finish may be formed on the outer bottom surface 52 of the case 13.
- the friction coefficient between the outer bottom surface 52 and the inner bottom surface 24 can be ensured because the friction coefficient of the outer bottom surface 52 becomes higher than when the outer bottom surface 52 is smooth.
- the matte surface of the outer bottom surface 52 of the case 13 can be formed by electric discharge machining or laser processing. However, when formed by shot peening, the outer bottom surface 52 of the case 13 is hardened and wear resistance is increased. The frictional resistance between the inner bottom surfaces 24 can be maintained for a long time.
- a taper outer peripheral surface 55 formed on the bottom portion 17 of the case 13 and a taper outer peripheral surface 55 formed on the bottom portion 17 of the case 13 is fitted to the taper inner peripheral surface 54 formed on the housing hole 6.
- the axial load may be received by the tapered inner peripheral surface 54.
- a recess 56 is provided on the outer bottom surface 52 of the case 13, leaving the periphery thereof, so that only the periphery of the outer bottom surface 52 of the case 13 is in contact with the inner bottom surface 24 of the accommodation hole 6. Also good.
- a recess (not shown) is provided on the inner bottom surface 24 of the accommodation hole 6 so as to leave its periphery, so that only the periphery of the inner bottom surface 24 of the accommodation hole 6 contacts the outer bottom surface 52 of the case 13. Good. Even in this case, since the frictional resistance generated between the outer bottom surface 52 of the case 13 and the inner bottom surface 24 of the accommodation hole 6 is concentrated on the outer diameter side, the frictional resistance necessary for preventing the rotation of the case 13 is ensured. It becomes possible to do.
- a small-diameter inner peripheral portion 57 having an inner diameter smaller than the outer diameter of the bottom portion 17 of the case 13 is formed in the receiving hole 6, and the bottom portion 17 of the case 13 is press-fitted into the small-diameter inner peripheral portion 57. (In other words, it may be inserted with a tightening margin).
- an iron base 59 constituting the inner bottom surface 24 of the accommodation hole 6 is incorporated in the accommodation hole 6, and when the axial load is applied to the case 13, the axial load is reduced. You may make it catch on the base 59.
- the inner bottom surface 24 of the accommodation hole 6 is iron, the inner bottom surface 24 of the accommodation hole 6 is not easily worn even when the cylinder head is made of aluminum. Therefore, the friction coefficient of the inner bottom surface 24 hardly decreases with time, and the frictional resistance between the bottom portion 17 of the case 13 and the inner surface of the accommodation hole 6 can be ensured.
- a bottomed cylindrical iron sleeve 61 constituting the accommodation hole 6 is press-fitted into a base hole 60 formed on the upper surface of the cylinder head 2 so that an axial load is applied to the case 13.
- the axial load may be received by the sleeve 61.
- the inner surface of the accommodation hole 6 is iron, the inner surface of the accommodation hole 6 is not easily worn even when the cylinder head 2 is formed of aluminum, and between the bottom portion 17 of the case 13 and the inner surface of the accommodation hole 6. The frictional resistance can be ensured. Further, since there is no difference in thermal expansion between the sleeve 61 and the case 13, the fitting force of the case 13 with respect to the accommodation hole 6 can be ensured even when the ambient temperature rises.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
2 シリンダヘッド
6 収容穴
7 アーム
13 ケース
14 雌ねじ
15 雄ねじ
16 アジャストスクリュ
17 底部
18 リターンスプリング
22 突出端
24 内底面
25 エア抜き孔
26 嵌合口
27 回り止め突起
28 Dカット部
30 貫通孔
31 二面取り部
32,35,37 回り止め突起
41,51 ラッシュアジャスタ
52 外底面
53 油膜排除溝
54 テーパ内周面
55 テーパ外周面
56 凹部
57 小径内周部
58 シート
59 台座
61 スリーブ
Claims (22)
- シリンダヘッド(2)の上面に開口した収容穴(6)に挿入される有底円筒状のケース(13)と、そのケース(13)の内周に形成された雌ねじ(14)にねじ係合する雄ねじ(15)を外周に有するアジャストスクリュ(16)と、そのアジャストスクリュ(16)と前記ケース(13)の底部(17)との間に組み込まれ、アジャストスクリュ(16)をケース(13)から上方に突出する方向に付勢するリターンスプリング(18)とを有し、前記アジャストスクリュ(16)のケース(13)からの突出端(22)で動弁装置のアーム(7)を揺動可能に支持するラッシュアジャスタにおいて、
前記ケース(13)の回転を防止する回り止め手段を設けたことを特徴とするラッシュアジャスタ。 - 前記回り止め手段が、前記ケース(13)の底部(17)に設けた回り止め突起(27)と、その回り止め突起(27)に嵌合し、前記収容穴(6)の内底面(24)に形成された嵌合口(26)とからなる請求項1に記載のラッシュアジャスタ。
- 前記回り止め突起が、外周にDカット部(28)を有する突起(27)である請求項2に記載のラッシュアジャスタ。
- 前記回り止め突起が、外周に二面取り部(31,31)を有する突起(32)である請求項2に記載のラッシュアジャスタ。
- 前記回り止め突起が、正多角柱状の突起(35)である請求項2に記載のラッシュアジャスタ。
- 前記回り止め突起が、ケース(13)の軸心に対して偏心した突起(37)である請求項2に記載のラッシュアジャスタ。
- 前記嵌合口(26)が、前記収容穴(6)の内底面(24)から外部に連通するエア抜き孔(25)の一端である請求項2から6のいずれかに記載のラッシュアジャスタ。
- 前記ケース(13)の底部(17)を上下に貫通する貫通孔(30)を設け、その貫通孔(30)の下端を前記回り止め突起(27)の先端に開口させた請求項7に記載のラッシュアジャスタ。
- 前記回り止め手段が、前記ケース(13)の底部(17)と前記収容穴(6)の内面との間の摩擦抵抗を確保してケース(13)の回転を防止する摩擦確保手段である請求項1に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記ケース(13)の外底面(52)に形成した油膜排除溝(53)である請求項9に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記ケース(13)の外底面(52)に形成した梨地である請求項9に記載のラッシュアジャスタ。
- 前記梨地をショットピーニングにより形成した請求項11に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記ケース(13)の底部(17)に形成された下方に縮径するテーパ外周面(55)と、前記収容穴(6)に形成された下方に縮径するテーパ内周面(54)とからなり、前記テーパ外周面(55)をテーパ内周面(54)に嵌合させた請求項9に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記ケース(13)の外底面(52)にその周縁を残して設けた凹部(56)、または、前記収容穴(6)の内底面(24)にその周縁を残して設けた凹部である請求項9に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記収容穴(6)に形成した小径内周部(57)であり、その小径内周部(57)に前記ケース(13)の底部(17)を圧入した請求項9に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記ケース(13)の外底面(52)と前記収容穴(6)の内底面(24)との間に挟み込んだゴム製またはエラストマ製のシート(58)である請求項9に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記収容穴(6)の内底面(24)を構成する鉄製の台座(59)である請求項9に記載のラッシュアジャスタ。
- 前記摩擦確保手段が、前記収容穴(6)を構成する有底円筒状の鉄製スリーブ(61)である請求項9に記載のラッシュアジャスタ。
- 前記リターンスプリング(18)は、前記ケース(13)から突出する方向の軸方向力をアジャストスクリュ(16)に付与する圧縮コイルばねである請求項1から18のいずれかに記載のラッシュアジャスタ。
- 前記リターンスプリング(18)は、前記ケース(13)から突出する方向の回転力をアジャストスクリュ(16)に付与するねじりばねである請求項1から18のいずれかに記載のラッシュアジャスタ。
- 前記ねじりばねが、ねじりコイルばね、ゼンマイばね、竹の子ばねのいずれかである請求項20に記載のラッシュアジャスタ。
- 前記雄ねじ(15)と雌ねじ(14)が、三角ねじ、台形ねじ、または鋸歯ねじである請求項1から21のいずれかに記載のラッシュアジャスタ。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/921,587 US20110036314A1 (en) | 2008-03-24 | 2009-03-16 | Lash adjuster |
DE112009000693T DE112009000693T5 (de) | 2008-03-24 | 2009-03-16 | Spielausgleichsvorrichtung |
Applications Claiming Priority (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008075950 | 2008-03-24 | ||
JP2008-075950 | 2008-03-24 | ||
JP2008-110991 | 2008-04-22 | ||
JP2008110991 | 2008-04-22 | ||
JP2008-257362 | 2008-10-02 | ||
JP2008257362A JP2009281376A (ja) | 2008-04-22 | 2008-10-02 | ラッシュアジャスタ |
JP2008-257342 | 2008-10-02 | ||
JP2008257342A JP2009257305A (ja) | 2008-03-24 | 2008-10-02 | ラッシュアジャスタ |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2009119362A1 true WO2009119362A1 (ja) | 2009-10-01 |
Family
ID=41113559
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2009/055002 WO2009119362A1 (ja) | 2008-03-24 | 2009-03-16 | ラッシュアジャスタ |
Country Status (1)
Country | Link |
---|---|
WO (1) | WO2009119362A1 (ja) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS615306U (ja) * | 1984-06-18 | 1986-01-13 | トヨタ自動車株式会社 | 内燃機関の動弁機構 |
JP2002235509A (ja) * | 2001-02-06 | 2002-08-23 | Otics Corp | 動弁装置のバルブクリアランス調整機構 |
JP2006132426A (ja) * | 2004-11-05 | 2006-05-25 | Ntn Corp | アーム式動弁装置 |
JP2006336585A (ja) * | 2005-06-03 | 2006-12-14 | Ntn Corp | アーム式動弁装置 |
JP2007100585A (ja) * | 2005-10-04 | 2007-04-19 | Otics Corp | 内燃機関の休止機構付きラッシュアジャスタ |
-
2009
- 2009-03-16 WO PCT/JP2009/055002 patent/WO2009119362A1/ja active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS615306U (ja) * | 1984-06-18 | 1986-01-13 | トヨタ自動車株式会社 | 内燃機関の動弁機構 |
JP2002235509A (ja) * | 2001-02-06 | 2002-08-23 | Otics Corp | 動弁装置のバルブクリアランス調整機構 |
JP2006132426A (ja) * | 2004-11-05 | 2006-05-25 | Ntn Corp | アーム式動弁装置 |
JP2006336585A (ja) * | 2005-06-03 | 2006-12-14 | Ntn Corp | アーム式動弁装置 |
JP2007100585A (ja) * | 2005-10-04 | 2007-04-19 | Otics Corp | 内燃機関の休止機構付きラッシュアジャスタ |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2009096353A1 (ja) | ラッシュアジャスタ | |
KR101895984B1 (ko) | 기계식 래시 어저스터 | |
JP4215663B2 (ja) | バルブクリアランス自動調整装置 | |
US20110036314A1 (en) | Lash adjuster | |
WO2009145169A1 (ja) | ラッシュアジャスタ | |
WO2009119362A1 (ja) | ラッシュアジャスタ | |
JP2009257304A (ja) | ラッシュアジャスタ | |
JP2009257305A (ja) | ラッシュアジャスタ | |
CN108026793B (zh) | 机械式间隙调整器 | |
WO2009125772A1 (ja) | ラッシュアジャスタ | |
JP2009281376A (ja) | ラッシュアジャスタ | |
WO2009093528A1 (ja) | ラッシュアジャスタ | |
WO2009093682A1 (ja) | アーム式動弁装置 | |
JP2009197790A (ja) | アーム式動弁装置 | |
JP2009216031A (ja) | ラッシュアジャスタ | |
JP2009203978A (ja) | アーム式動弁装置 | |
JP2010065615A (ja) | ラッシュアジャスタ | |
JP2009243465A (ja) | ラッシュアジャスタ | |
JP2009203975A (ja) | ラッシュアジャスタ | |
JP2009174341A (ja) | ラッシュアジャスタ | |
JP2009270500A (ja) | ラッシュアジャスタ | |
JP2009270505A (ja) | ラッシュアジャスタ | |
JP2009185682A (ja) | ラッシュアジャスタ | |
JP2009174487A (ja) | ラッシュアジャスタ | |
JP2009228566A (ja) | ラッシュアジャスタ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 09723753 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 12921587 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120090006930 Country of ref document: DE |
|
RET | De translation (de og part 6b) |
Ref document number: 112009000693 Country of ref document: DE Date of ref document: 20110324 Kind code of ref document: P |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 09723753 Country of ref document: EP Kind code of ref document: A1 |