WO2009093682A1 - Arm type valve gear device - Google Patents
Arm type valve gear device Download PDFInfo
- Publication number
- WO2009093682A1 WO2009093682A1 PCT/JP2009/051060 JP2009051060W WO2009093682A1 WO 2009093682 A1 WO2009093682 A1 WO 2009093682A1 JP 2009051060 W JP2009051060 W JP 2009051060W WO 2009093682 A1 WO2009093682 A1 WO 2009093682A1
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- WO
- WIPO (PCT)
- Prior art keywords
- arm
- housing
- screw
- recess
- type valve
- 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
Definitions
- This invention relates to an arm type valve operating apparatus in an internal combustion engine.
- 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 is generated due to the change in the gap.
- a lash adjuster is often incorporated in the valve operating device, and the lash adjuster often absorbs changes in the gaps between the components of the valve operating device.
- a cylindrical housing inserted into a receiving hole opened on the upper surface of the cylinder head, an adjustment screw having a male screw on the outer periphery that engages with a female screw formed on the inner periphery of the housing,
- Patent Documents 1 and 2 One having a return spring that biases the adjustment screw in a direction protruding upward from the housing is known (Patent Documents 1 and 2).
- Patent Document 1 a compression coil spring that applies an axial force in a direction protruding from the housing 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 housing is used as a return spring.
- the protruding end of the adjusting screw from the housing is formed in a hemispherical shape, and the protruding end fits into a recess formed in the arm.
- the protruding end of the adjusting screw contacts the inner surface of the recess of the arm and supports the arm so as to be able to swing.
- the coefficient of friction between the adjusting screw's protruding end and arm recess decreases, so the adjust screw can easily rotate and move in the pushing direction during engine operation. Become. In this case, since the swing fulcrum of the arm is shifted, the valve lift amount may be reduced, or the valve may be shockedly seated on the valve seat to generate noise.
- lubrication between the male screw of the adjusting screw and the female screw of the housing is also performed by engine oil splashed on the arm.
- the upper end surface of the housing is located above the upper surface of the cylinder head. The projecting arrangement makes it difficult for engine oil splashed on the arm to enter between the housing and the adjusting screw. Therefore, the lubrication between the male screw of the adjusting screw and the female screw of the housing is poor, and the male screw and the female screw are likely to be seized and worn.
- the friction coefficient between the male screw and the female screw decreases, so that the adjustment screw rotates and easily moves in the pushing direction during engine operation.
- the valve lift amount may be reduced, or the valve may be shockedly seated on the valve seat to generate noise.
- the problem to be solved by the present invention is to prevent the rotational resistance of the adjustment screw from being reduced by wear of the protruding end of the adjustment screw, wear of the recess of the arm, or wear of the male screw and the female screw.
- an oil passage hole is provided that penetrates the arm up and down, and a lower end of the oil passage hole is opened in the recess of the arm, and the engine oil enters the recess of the arm through the oil passage hole.
- the engine oil splashed on the arm is introduced into the recess through the oil passage hole, so that the lubricity between the protruding end of the adjustment screw and the recess of the arm is improved, and the adjustment screw The protruding end and the arm recess are less likely to wear.
- This arm type valve gear can add the following structure. 1) By offsetting the center of curvature of the recess of the arm and the center of curvature of the protruding end of the adjusting screw, the protruding end of the adjusting screw has a wedge effect. 2) A concave surface or a flat surface is formed at the center of the protruding end of the adjusting screw, and the diameter of the concave surface or the flat surface is larger than half of the diameter of the protruding end of the adjusting screw. 3) The surface of the protruding end of the adjusting screw is a matte surface having a surface roughness Ra of 0.4 or more.
- the inner surface of the concave portion of the arm is a satin surface having a surface roughness Ra of 0.4 or more.
- An oil film exclusion groove is formed on the surface of the protruding end of the adjustment screw.
- An oil film removal groove is formed on the inner surface of the recess of the arm.
- the recess of the arm has an arc shape in cross section along the plane including the axis of the adjustment screw, and the center of the arc of the recess is such that the arc radius of the recess intersects with the axis of the adjustment screw.
- the protruding end of the adjusting screw is arranged at a position offset from the axis, and the cross-sectional shape along the plane including the axis of the adjusting screw is an arc shape having a center on the axis of the adjusting screw.
- the arc radius of the end is smaller than the arc radius of the recess of the arm.
- the satin mentioned in 3) and 4) above is a surface composed of uniform unevenness without directionality.
- the oil film removal groove may be formed so as to extend in the circumferential direction or may be formed so as to extend in a spiral shape.
- the formation of these oil film exclusion grooves may be performed by cutting, but if the rolling is performed by rolling, the strength of the protruding end of the adjusting screw is increased and the durability is improved.
- the oil film exclusion groove may be formed so as to extend in the axial direction. If a plurality of the oil film removal grooves are formed at intervals in the circumferential direction, a stable oil film removal effect can be exhibited regardless of the rotation angle of the adjusting screw. When the oil film exclusion groove is formed by forging, the strength of the protruding end of the adjusting screw is increased and the durability is improved.
- the upper end surface of the housing is disposed below the upper surface of the cylinder head so that the engine oil splashed on the arm accumulates on the upper end surface of the housing. be able to.
- the engine oil accumulated on the upper end surface of the housing enters between the male screw of the adjusting screw and the female screw of the housing, so that the lubricity between the male screw of the adjusting screw and the female screw of the housing is improved, and the male screw and the female screw are improved. Is less likely to wear.
- annular recess surrounding the accommodation hole can be provided on the upper surface of the cylinder head.
- the inner surface of the annular recess is a tapered inclined surface that guides the engine oil accumulated in the annular recess to the accommodation hole.
- a cylindrical protrusion surrounding the annular recess is provided on the upper surface of the cylinder head.
- the upper end surface of the housing is a tapered inclined surface that guides engine oil accumulated on the upper end surface of the housing to the inner diameter side.
- a through hole that vertically penetrates the bottom of the housing is provided, and an oil drain hole that communicates with the through hole is provided on the bottom surface of the accommodation hole.
- the present invention can be applied to an arm type valve gear that uses a compression coil spring that applies an axial force in a direction protruding from a housing to an adjustment screw as the return spring.
- the male screw and the female screw are serrated. Screws can be employed.
- the present invention can also be applied to an arm type valve gear that uses a torsion spring that applies a rotational force in a direction protruding from a housing to an adjustment screw as the return spring.
- the male screw and the female screw are Sawtooth screws, triangular screws, or trapezoidal screws can be employed.
- the torsion spring include a torsion coil spring, a spring, and a bamboo spring.
- the adjustment screw includes a pivot member inserted in the housing so as to be slidable in the axial direction, a male screw member supporting an insertion end of the pivot member into the housing, and having the male screw on an outer periphery, and the pivot member and the male screw. It can be comprised with the elastic member pinched
- a square hole is formed at the insertion end of the pivot member into the housing, a square shaft that fits into the square hole is formed in the male screw member, and the pivot is formed by fitting the square shaft and the square hole. It is preferable that the member and the male screw member rotate together. If it does in this way, since a male screw member can be rotated by rotation operation of a pivot member, the operation
- the oil passage hole for introducing the engine oil splashed into the recess is provided in the arm, the lubrication between the protruding end of the adjustment screw and the recess of the arm is good.
- the protruding end of the screw and the recess of the arm are less likely to wear. Therefore, the coefficient of friction between the protruding end of the adjusting screw and the recess of the arm is unlikely to decrease, and the rotational resistance of the adjusting screw is unlikely to decrease.
- the curvature radius of the recess of the arm in a cross section along the plane including the axis of the adjustment screw is made larger than the curvature radius of the protruding end of the adjustment screw, and the curvature center of the recess of the arm and the adjustment screw are adjusted.
- the projecting end of the adjusting screw has a wedge effect.When the projecting end of the adjusting screw is pressed by the recess of the arm, the projecting end of the adjusting screw The wedge effect fits into the recess of the arm.
- a concave surface or a flat surface is formed in the center of the protruding end of the adjusting screw, and the diameter of the concave surface or the flat surface is larger than half the diameter of the protruding end of the adjusting screw. Since the arm recess comes into contact with the outer diameter side, the frictional resistance between the protruding end of the adjusting screw and the recess of the arm is large. Even when FM oil is used as the engine oil, the protruding end of the adjusting screw and the arm It is possible to ensure a frictional resistance between the concave portion and the concave portion.
- the surface of the protruding end of the adjusting screw that has a matte surface with a surface roughness of Ra 0.4 or more is provided with a concave portion of the arm and the adjusting screw when a load in the pushing direction is applied from the arm to the adjusting screw. Since the engine oil existing between the projecting ends escapes into the gap between the irregularities of the satin finish, it is difficult to form an oil film due to the squeeze effect between the recesses of the arm and the projecting ends of the adjustment screw. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
- the inner surface of the recess of the arm having a satin finish with a surface roughness of Ra 0.4 or more can be applied to the recess of the arm and the protruding end of the adjustment screw when a load in the pushing direction is applied from the arm to the adjustment screw. Since the engine oil existing between them escapes into the gaps between the uneven surfaces of the matte surface, it is difficult to form an oil film due to the squeeze effect between the recesses of the arms and the protruding ends of the adjustment screws. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
- the oil screw exclusion groove formed on the surface of the protruding end of the adjusting screw exists between the recess of the arm and the protruding end of the adjusting screw when a load in the pushing direction is applied from the arm to the adjusting screw. Since the engine oil escapes into the oil film exclusion groove, an oil film due to the squeeze effect is hardly formed between the recess of the arm and the protruding end of the adjustment screw. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
- an oil film exclusion groove formed on the inner surface of the recess of the arm also has engine oil that exists between the recess of the arm and the protruding end of the adjustment screw when a load in the pushing direction is applied from the arm to the adjustment screw. Since it escapes into the oil film removal groove, an oil film due to the squeeze effect is hardly formed between the recess of the arm and the protruding end of the adjustment screw. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
- the upper end surface of the housing is disposed below the upper surface of the cylinder head, and engine oil splashed on the arm is accumulated on the upper end surface of the housing. Since the engine oil collected in the screw enters between the male screw of the adjusting screw and the female screw of the housing, the lubricating between the male screw of the adjusting screw and the female screw of the housing is good, and seizure and wear of the male screw and the female screw are unlikely to occur. Therefore, the coefficient of friction between the male screw and the female screw is unlikely to decrease, and the rotational resistance of the adjusting screw is unlikely to decrease.
- the engine oil also accumulates in the annular recess, so that a large amount of engine oil accumulates above the housing. Therefore, even when the engine oil splashed on the arm is small, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
- the engine oil in the annular recess flows toward the accommodation hole due to the inclination of the inner surface of the annular recess. Even when the amount is reduced, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
- the engine oil can be stored in the space in the cylindrical protrusion, so that the engine oil is stored above the housing. The amount of more. Therefore, even when the engine oil splashed on the arm is small, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
- the engine oil accumulated on the upper end surface of the housing flows to the inner diameter side due to the inclination of the upper end surface, so the engine oil accumulated on the upper end surface of the housing Even when the amount is reduced, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
- a through hole that vertically penetrates the bottom of the housing and an oil drain hole that communicates with the through hole on the bottom surface of the housing hole passes between the male screw of the adjusting screw and the female screw of the housing. Then, the engine oil flowing into the housing is discharged from the housing through the through hole and the oil drain hole. For this reason, the contamination and wear powder mixed in the engine oil are unlikely to stay between the male screw of the adjusting screw and the female screw of the housing, and the male screw and the female screw are not easily worn.
- FIG. 1 is an enlarged cross-sectional view in the vicinity of a lash adjuster of the valve gear shown in FIG.
- the expanded sectional view which shows the modification of the protrusion end of the adjusting screw shown in FIG.
- FIG. 6 is an enlarged sectional view in the vicinity of an adjusting screw protruding end showing an arm type valve gear according to a third embodiment of the present invention.
- FIG. 6 is an enlarged cross-sectional view showing a modification in which the oil film removal groove shown in FIG. 6 is formed on the arm side.
- FIG. 6 is an enlarged sectional view showing another modified example in which the oil film exclusion groove shown in FIG. 6 is formed on the arm side.
- FIG. 6 is an enlarged cross-sectional view showing still another modified example in which the oil film exclusion groove shown in FIG. 6 is formed on the arm side.
- FIG. 13 is an enlarged cross-sectional view showing a modification in which the inner surface of the annular recess shown in FIG. 13 is a tapered inclined surface.
- FIG. 14 is an enlarged cross-sectional view showing a modification in which a cylindrical projection surrounding the annular recess is provided on the upper surface of the cylinder head shown in FIG.
- FIG. 14 is an enlarged sectional view showing a modification in which the upper end surface of the housing shown in FIG. 14 is a tapered inclined surface.
- FIG. 2 is an enlarged sectional view showing a modification of the return spring shown in FIG. FIG.
- FIG. 17 is an enlarged sectional view showing a modification of the male screw and the female screw shown in FIG.
- FIG. 17 is an enlarged sectional view showing another modification example of the male screw and the female screw shown in FIG.
- 20 is an enlarged cross-sectional view showing a modification of the return spring shown in FIG. 20 is an enlarged cross-sectional view showing another modification of the return spring shown in FIG.
- FIG. 20 is an enlarged sectional view showing still another modification of the return spring shown in FIG. Sectional view along the line XXIV-XXIV in FIG.
- FIG. 1 shows an arm type valve operating apparatus according to a first embodiment of the present invention.
- This valve operating apparatus includes a valve 3 provided in an intake port 2 of a cylinder head 1 of an engine, a valve stem 4 connected to the valve 3, an arm 6 that swings according to rotation of a cam 5, a lash And an adjuster 7.
- the valve stem 4 extends upward from the valve 3 and slidably penetrates the cylinder head 1.
- An annular spring retainer 8 is fixed to the upper outer periphery of the valve stem 4, and a valve spring 9 is incorporated between the lower surface of the spring retainer 8 and the upper surface of the cylinder head 1.
- the valve spring 9 urges the valve stem 4 upward via the spring retainer 8, and the valve 3 is seated on the valve seat 10 by the urging force.
- the lash adjuster 7 is screw-engaged with a cylindrical housing 12 inserted into a receiving hole 11 opened in the upper surface 1 a of the cylinder head 1 and a female screw 13 formed on the inner periphery of the housing 12.
- An adjustment screw 15 having a male screw 14 on the outer periphery of the lower part, a bottom member 16 fixed to the lower end of the housing 12, and a return spring 17 incorporated between the adjustment screw 15 and the bottom member 16.
- the male screw 14 and the female screw 13 are formed in a sawtooth shape having an asymmetric cross section along the axis, and the pressure-side flank 18 that receives pressure when a load in the direction of pushing the adjusting screw 15 into the housing 12 is applied.
- the flank angle is larger than the flank angle of the play side flank 19.
- the return spring 17 is a compression coil spring.
- the return spring 17 has a lower end supported by the bottom member 16 and an upper end that applies an axial force in a direction protruding from the housing 12 via the spring seat 20 to the adjusting screw 15. Due to the axial force, the adjusting screw 15 is biased in a direction protruding upward from the housing 12.
- the arm 6 has a recess 22 that fits into the protruding end 21 of the adjusting screw 15 from the housing 12 on the lower surface of one end, and swings around the protruding end 21 of the adjusting screw 15. It is supported movably.
- the lower surface of the other end of the arm 6 is in contact with the upper end of the valve stem 4, and a roller 23 that is in contact with the cam 5 disposed above the arm 6 is attached to the center of the arm 6.
- the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 are both formed in a hemispherical shape, and the protruding end 21 of the adjusting screw 15 is formed on the inner surface of the recessed portion 22 of the arm 6. In contact.
- a flat surface 24 is provided at the center of the protruding end 21 of the adjusting screw 15. The diameter D 2 of the flat surface 24 is larger than half of the diameter D 1 of the protruding end 21.
- the arm 6 has an oil passage hole 25 penetrating the end of the arm 6 up and down.
- the lower end of the oil passage hole 25 opens into the recess 22 of the arm 6, and engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25.
- the length from the upper end surface 12a of the housing 12 to the lower end surface 16a of the bottom member 16 is shorter than the length of the accommodation hole 11 (the length from the upper surface 1a of the cylinder head 1 to the bottom of the accommodation hole 11).
- the upper end surface 12a of the housing 12 is arranged so as to be recessed below the upper surface 1a of the cylinder head 1 so that the engine oil splashed on the arm 6 accumulates on the upper end surface 12a of the housing 12. It has become.
- the bottom member 16 has a through hole 26 penetrating vertically, and an oil drain hole 27 communicating with the through hole 26 is formed on the bottom surface of the accommodation hole 11. Therefore, the engine oil that has flowed into the housing 12 from the upper end surface 12a of the housing 12 through the gap between the male screw 14 and the female screw 13 is discharged from the housing 12 through the through hole 26 and the oil draining hole 27 in order.
- this arm type valve operating apparatus has the flat surface 24 formed in the center of the protrusion end 21 of the adjustment screw 15, the protrusion end 21 of the adjustment screw 15 and the recessed part 22 of the arm 6 are outside diameter side. Contact. For this reason, the friction resistance between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 is large, and even when engine oil containing organic molybdenum (hereinafter referred to as “FM oil”) is used as engine oil. The frictional resistance between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 can be ensured.
- the organic molybdenum include molybdenum dithiocarbamate (MoDTC) and molybdenum dithiophosphate (MoDTP).
- the engine oil splashed on the arm 6 and the cylinder head 1 accumulates on the upper end surface 12a of the housing 12, so that the engine oil easily enters between the male screw 14 and the female screw 13. Therefore, lubrication between the male screw 14 and the female screw 13 is good, and seizure and wear of the male screw 14 and the female screw 13 are difficult to occur.
- the engine oil that has flowed into the housing 12 through between the male screw 14 and the female screw 13 is discharged from the housing 12 through the through hole 26 and the oil draining hole 27. Therefore, the contamination and wear powder mixed in the engine oil are less likely to stay between the male screw 14 and the female screw 13, and the male screw 14 and the female screw 13 are less likely to wear.
- the protruding end 21 of the adjusting screw 15 is formed such that a cross-sectional shape along a plane including the axis L of the adjusting screw 15 has an arc shape having a center O 1 on the axis L.
- the recess 22 of the arm 6 also has an arc shape in cross section along the plane including the axis L of the adjusting screw 15, and the arc center O 2 of the recess 22 intersects with the axis L of the arc radius A 2 of the recess 22. Thus, it is arranged at a position offset from the axis L.
- the arc radius A 1 of the protruding end 21 is smaller than the arc radius A 2 of the recess 22.
- this arm type valve gear is fitted so that the protruding end 21 bites into the recessed portion 22 by the wedge effect when the protruding end 21 of the adjusting screw 15 is pressed by the recessed portion 22 of the arm 6. Therefore, a large frictional resistance is generated between the protruding end 21 and the recessed portion 22, and even when FM oil is used as the engine oil, the frictional resistance between the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 is reduced. Can be secured.
- this arm type valve operating device is longer in the axial direction of the adjusting screw 15 and the housing 12 than an arm type valve operating device in which the center of curvature O 2 of the recess 22 and the center of curvature O 1 of the protruding end 21 are not offset. Therefore, the weight can be reduced.
- the surface of the protruding end 21 of the adjusting screw 15 is a satin finish having a surface roughness of Ra 0.4 or more by performing shot peening.
- This satin can be formed by shot peening using sharp-angled media, and when the adjustment screw 15 is subjected to heat treatment (for example, carburizing or nitriding), the shot peening is performed before the heat treatment. Can be formed.
- the surface roughness Ra is in accordance with JIS B0601 (product geometric characteristic specification (GPS) -surface property: contour curve method-terminology, definition and surface property parameter).
- this arm type valve operating apparatus when the meshing length of the male screw 14 and the female screw 13 is set short, the surface pressure acting on the pressure side flank 18 of the male screw 14 and the female screw 13 is increased, and the wear of the pressure side flank 18 is increased. As a result, the frictional resistance between the male screw 14 and the female screw 13 tends to decrease, but since the frictional resistance between the protruding end 21 and the recess 22 is ensured, the adjustment screw 15 moves excessively in the pushing direction during engine operation. There is nothing to do. Therefore, this arm type valve operating device can suppress the axial length of the adjusting screw 15 and the housing 12 as compared with the arm type valve operating device in which the surface of the protruding end of the adjusting screw is smooth. Is possible.
- the surface roughness Ra of the protruding end 21 is ensured.
- Table 1 the stability of the valve lift amount (movement stroke of the valve 3) was tested for each lash adjuster incorporating the adjustment screw 15, and the results shown in Table 1 were obtained. . From Table 1, when the surface roughness Ra of the protruding end 21 is in the range of 0.4 or more and 25 or less, the stability of the valve lift amount is excellent, and the surface roughness Ra of the protruding end 21 is 0.4. It can be seen that the adjustment screw 15 is less likely to move in the push-in direction than in the range below the lower limit.
- the surface of the protruding end 21 of the adjusting screw 15 is a matte surface having a surface roughness Ra of 0.4 or more.
- the inner surface of the recess 22 may be a satin having a surface roughness Ra of 0.4 or more. Even in this case, it is difficult to form an oil film due to the squeeze effect between the recessed portion 22 of the arm 6 and the protruding end 21 of the adjusting screw 15, and the gap between the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 is reduced. Frictional resistance can be ensured.
- a plurality of oil film exclusion grooves 29 extending in the circumferential direction are formed on the surface of the projecting end 21 at intervals in the axial direction.
- the engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25 as in the first embodiment, so that the projecting end 21 of the adjustment screw 15 and the arm
- the lubrication between the six recesses 22 is good. Therefore, the wear of the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 does not easily progress, and the friction coefficient between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 is unlikely to decrease.
- the oil film removal groove 29 at the protruding end 21 of the adjustment screw 15 may be formed to extend in a spiral shape. Even in this case, the engine oil existing between the recess 22 of the arm 6 and the protruding end 21 of the adjustment screw 15 escapes into the oil film removal groove 29, so that an oil film due to the squeeze effect can be prevented.
- the oil film exclusion groove 29 extending in a spiral shape is formed so that the lower end thereof is exposed to the outside of the recess 22, the engine oil in the oil film exclusion groove 29 is discharged from the lower end of the oil film exclusion groove 29. Get higher.
- the formation of the oil film exclusion groove 29 described above may be performed by cutting, but if it is performed by rolling, the strength of the protruding end 21 of the adjusting screw 15 is increased, and the durability of the protruding end 21 can be improved.
- the oil film exclusion groove 29 may be formed to extend in the axial direction.
- the oil film exclusion groove 29 extending in the axial direction may be formed by cutting. However, if forging is performed, the strength of the protruding end 21 of the adjusting screw 15 is increased, and the durability can be improved.
- the oil film removal groove 29 is formed on the surface of the protruding end 21 of the adjustment screw 15.
- the oil film removal groove 30 is formed on the inner surface of the recess 22 of the arm 6. May be. Even in this case, the engine oil existing between the recess 22 of the arm 6 and the projecting end 21 of the adjustment screw 15 escapes into the oil film removal groove 30, so that an oil film due to the squeeze effect can be prevented.
- the oil film removal groove 30 may be formed to extend in the circumferential direction on the inner surface of the recess 22 of the arm 6, and as shown in FIG. 11, the inner surface of the recess 22 of the arm 6. 12 may be formed so as to extend in a spiral shape, or may be formed so as to extend in the axial direction on the inner surface of the recess 22 of the arm 6 as shown in FIG.
- an annular step is formed on the upper surface 1a of the cylinder head 1.
- an annular recess 31 surrounding the accommodation hole 11 may be provided.
- the engine oil also accumulates in the annular recess 31, so that the amount of engine oil that accumulates above the housing 12 increases. Therefore, even when the engine oil splashed on the arm 6 is small, the space between the male screw 14 and the female screw 13 can be stably lubricated.
- the inner surface of the annular recess 31 is tapered to guide the engine oil accumulated in the annular recess 31 to the accommodation hole 11. It is good also as a shape-like inclined surface. In this way, since the engine oil in the annular recess 31 flows toward the accommodation hole 11 due to the inclination of the inner surface of the annular recess 31, the male screw is provided even when the amount of engine oil accumulated in the annular recess 31 decreases. 14 and the internal thread 13 can be stably lubricated. Further, when the housing 12 is inserted into the accommodation hole 11, the housing 12 is guided to the accommodation hole 11 on the inner surface of the annular recess 31, so that the assembly operation of the valve operating device is easy.
- a cylindrical protrusion 32 surrounding the annular recess 31 may be provided on the upper surface 1 a of the cylinder head 1.
- the engine oil can be stored in the space in the cylindrical projection 32, so that the amount of the engine oil stored above the housing 12 is increased. Therefore, even when the engine oil splashed on the cylinder head 1 is small, the space between the male screw 14 and the female screw 13 can be stably lubricated.
- a cylindrical projection (not shown) surrounding the annular recess 31 can be provided on the upper surface 1a of the cylinder head 1 shown in FIG.
- the upper end surface 12a of the housing 12 is a tapered inclined surface that guides engine oil accumulated on the upper end surface 12a of the housing 12 to the inner diameter side. In this way, since the engine oil collected on the upper end surface 12a of the housing 12 flows to the inner diameter side due to the inclination of the upper end surface 12a, even when the amount of engine oil collected on the upper end surface 12a of the housing 12 decreases, The space between the male screw 14 and the female screw 13 can be stably lubricated.
- the upper end surface 12a of the housing 12 shown in FIGS. 12 and 13 may be a tapered inclined surface that guides engine oil accumulated on the upper end surface 12a of the housing 12 to the inner diameter side.
- the annular recess 31 may be formed by cutting the cylinder head 1. However, when the die is formed by aluminum die casting of the cylinder head 1, the cost is low.
- a compression coil spring is used as the return spring 17 that urges the adjustment screw 15 in a direction protruding upward from the housing 12, but a torsion coil spring may be used as shown in FIG. .
- the return spring 17 has a lower end locked in a locking hole 33 formed in the bottom member 16, and an upper end locked in a locking hole 34 formed in the adjusting screw 15. Due to the torsional deformation, rotational force in a direction protruding from the housing 12 is applied to the adjusting screw 15.
- a torsion spring for example, a spring spring or a bamboo spring
- a torsion coil spring can be employed as the return spring 17.
- the male screw 14 on the outer periphery of the adjustment screw 15 and the female screw 13 on the inner periphery of the housing 12 may employ vertically symmetrical triangular screws as shown in FIG. As shown in FIG. 19, a vertically symmetrical trapezoidal screw may be employed.
- the adjusting screw 15 supports a pivot member 15A inserted into the housing 12 so as to be slidable in the axial direction, an insertion end of the pivot member 15A into the housing 12, and a male screw 14 on the outer periphery. And a spring washer 15C sandwiched between the pivot member 15A and the male screw member 15B.
- the spring washer 15C for example, a disc spring washer or a corrugated washer can be used.
- the pivot member 15A has a square hole 35 formed at the center of the insertion end into the housing 12.
- the male screw member 15B is formed with a square shaft 36 that fits into the square hole 35. When the pivot member 15A is rotated, the pivot member 15A and the male screw member 15B are fitted by fitting the square shaft 36 and the square hole 35. Are designed to rotate together.
- the return spring 17 is a torsion coil spring.
- the return spring 17 has a lower end locked in a locking hole 33 formed in the bottom member 16, and an upper end locked in a locking hole 34 formed in the male screw member 15B.
- the rotational force in the direction in which the pivot member 15A protrudes from the housing 12 is applied to the male screw member 15B.
- the engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25 formed in the arm 6 as in the first embodiment.
- Lubrication between the projecting end 21 from the housing 12 and the recess 22 of the arm 6 is good, and wear of the projecting end 21 and the recess 22 does not easily progress.
- Other effects are the same as those of the first embodiment.
- this arm type valve operating system is configured such that when the engine is stopped at a high temperature and thereafter the engine is cooled to cause a contraction difference between the constituent members of the valve operating apparatus, the male screw member 15B and the pivot member 15A When the spring washer 15C in between 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 3 and the valve seat 10, and compression leakage does not occur.
- the pivot member 15A and the male screw member 15B rotate integrally by fitting the square shaft 36 and the square hole 35. Therefore, the male screw member can be rotated by rotating the pivot member 15A. 15B can be rotated. Therefore, the work of assembling the male screw member 15B in the housing 12 is easier than that in which the square shaft 36 and the square hole 35 are not provided.
- the spring washer 15C is used as an elastic member sandwiched between the pivot member 15A and the male screw member 15B.
- another elastic member for example, a compression coil spring
- a compression coil spring may be used instead of the spring washer 15C.
- the return spring 17 When a torsion coil spring is used as the return spring 17, the return spring 17 may be a cylinder wound as shown in FIG. 20, or may be a cone wound as shown in FIG. May be.
- a torsion spring for example, a spring spring or a bamboo spring
- the torsion coil spring may be employed.
- the return spring 17 is a spring spring in which a thin plate material is wound in a spiral shape.
- the return spring 17 has a large-diameter end that is prevented from rotating by the bottom member 16 of the housing 12, and a small-diameter end that is inserted into a slit formed in the projection 37 at the insertion end of the male screw member 15B into the housing 12,
- the rotational force in the direction in which the pivot member 15A protrudes from the housing 12 is applied to the male screw member 15B by torsional deformation.
- the external thread 14 on the outer periphery of the external thread member 15B and the internal thread 13 on the inner periphery of the housing 12 are vertically symmetrical triangular screws.
- the return spring 17 is a bamboo shoot spring in which a thin plate material is spirally wound.
- the return spring 17 has a large-diameter end that is prevented from rotating by the bottom member 16 of the housing 12, and a small-diameter end that is inserted into a slit formed in the projection 38 at the insertion end of the male screw member 15B into the housing 12, Due to the torsional deformation, a rotational force in a direction in which the pivot member 15A protrudes from the housing 12 is applied to the male screw member 15B.
- the external thread 14 on the outer periphery of the external thread member 15B and the internal thread 13 on the inner periphery of the housing 12 are vertically symmetrical trapezoidal screws.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
An arm type valve gear device in which rotational resistance of an adjusting screw is not reduced by abrasion of the screw. The arm type valve gear device has a housing (12) inserted in a housing hole (11) open in the upper surface (1a) of a cylinder head (1), an adjusting screw (15) having on the outer periphery thereof a male screw thread (14) engaging with a female screw thread (13) formed in the inner periphery of the housing (12), a return spring (17) for urging the adjusting screw (15) in the direction in which the adjusting screw protrudes from the housing (12), and an arm (6) having a recess (22) in which that protruding end (21) of the adjusting screw (15) which protrudes from the housing (12) is fitted. The protruding end (21) of the adjusting screw (15) is made to be in contact with the inner surface of the recess (22). The arm (6) has an oil path hole (25) vertically penetrating through the arm, the lower end of the oil path hole (25) is open in the recess (22), and engine oil is introduced into the recess (22) through the oil path hole (25).
Description
この発明は、内燃機関におけるアーム式動弁装置に関する。
This invention relates to an arm type valve operating apparatus in an internal combustion engine.
エンジンの吸気ポートまたは排気ポートに設けたバルブを動作させる動弁装置として、一端部を支点として揺動可能に支持されたアームの中央部をカムで押し下げ、そのアームの他端部でバルブステムを押し下げるようにしたアーム式動弁装置が知られている。
As a 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. 2. Description of the Related Art Arm type valve gears that are pushed down are known.
この動弁装置は、エンジン作動中、動弁装置の構成部材間に生じる熱膨張差によって、動弁装置の構成部材間の隙間が変化し、その隙間の変化によって異音や圧縮漏れを生じるおそれがある。また、動弁装置の摺動部が摩耗しても、動弁装置の構成部材間の隙間が変化し、その隙間の変化によって異音を生じるおそれがある。
In this valve operating apparatus, 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 is generated due to the change in the gap.
この異音や圧縮漏れを防止するため、ラッシュアジャスタを動弁装置に組み込み、そのラッシュアジャスタで動弁装置の構成部材間の隙間の変化を吸収することが多い。
In order to prevent this abnormal noise and compression leakage, a lash adjuster is often incorporated in the valve operating device, and the lash adjuster often absorbs changes in the gaps between the components of the valve operating device.
このようなラッシュアジャスタとして、シリンダヘッドの上面に開口した収容穴に挿入される筒状のハウジングと、そのハウジングの内周に形成された雌ねじにねじ係合する雄ねじを外周に有するアジャストスクリュと、そのアジャストスクリュを前記ハウジング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とを有するものが知られている(特許文献1,2)。
As such a lash adjuster, a cylindrical housing inserted into a receiving hole opened on the upper surface of the cylinder head, an adjustment screw having a male screw on the outer periphery that engages with a female screw formed on the inner periphery of the housing, One having a return spring that biases the adjustment screw in a direction protruding upward from the housing is known (Patent Documents 1 and 2).
ここで、特許文献1では、ハウジングから突出する方向の軸方向力をアジャストスクリュに付与する圧縮コイルばねがリターンスプリングとして用いられている。また、特許文献2では、ハウジングから突出する方向の回転力をアジャストスクリュに付与するねじりばねがリターンスプリングとして用いられている。
Here, in Patent Document 1, a compression coil spring that applies an axial force in a direction protruding from the housing 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 housing is used as a return spring.
これらのラッシュアジャスタは、アジャストスクリュのハウジングからの突出端が半球状に形成されており、その突出端が、アームに形成された凹部に嵌合する。また、アジャストスクリュの突出端は、アームの凹部の内面に接触して、アームを揺動可能に支持する。
In these lash adjusters, the protruding end of the adjusting screw from the housing is formed in a hemispherical shape, and the protruding end fits into a recess formed in the arm. The protruding end of the adjusting screw contacts the inner surface of the recess of the arm and supports the arm so as to be able to swing.
また、エンジン作動中、アジャストスクリュには押し込み方向の荷重が負荷されるが、アジャストスクリュの雄ねじとハウジングの雌ねじの間の摩擦抵抗と、アジャストスクリュの突出端とアームの凹部の間の摩擦抵抗とによってアジャストスクリュの回転が防止され、その結果、アジャストスクリュの軸方向位置が固定される。
In addition, while the engine is running, a load in the pushing direction is applied to the adjust screw, but the friction resistance between the male screw of the adjustment screw and the female screw of the housing, and the friction resistance between the protruding end of the adjustment screw and the recess of the arm Prevents the adjustment screw from rotating, and as a result, the axial position of the adjustment screw is fixed.
一方、動弁装置の熱膨張などによって、アームとシリンダヘッドの相対位置が変化したときは、その位置変化に応じて、アジャストスクリュがハウジング内を回転しながら軸方向に移動し、動弁装置の構成部材間の隙間の変化を吸収する。
特開2005-273510号公報
実開昭64-34407号公報
On the other hand, when the relative position of the arm and the cylinder head changes due to thermal expansion of the valve operating device, etc., the adjusting screw moves in the axial direction while rotating in the housing 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
ところで、上記の動弁装置は、エンジン作動中、アームにエンジンオイルがはねかけられるが、アームの凹部は、アームの下面に形成されているので、アームの凹部内にエンジンオイルが入り込みにくい。そのため、アジャストスクリュの突出端とアームの凹部の間の潤滑が悪く、アジャストスクリュの突出端とアームの凹部の摩耗が進行しやすかった。
By the way, in the valve operating device described above, engine oil is splashed onto the arm during engine operation. However, since the arm recess is formed on the lower surface of the arm, the engine oil is less likely to enter the arm recess. For this reason, the lubrication between the protruding end of the adjusting screw and the concave portion of the arm is poor, and wear of the protruding end of the adjusting screw and the concave portion of the arm is likely to proceed.
アジャストスクリュの突出端とアームの凹部の摩耗が進行すると、アジャストスクリュの突出端とアームの凹部の間の摩擦係数が低下するので、エンジン作動中、アジャストスクリュが回転して押し込み方向に移動しやすくなる。この場合、アームの揺動支点がずれるので、バルブリフト量が小さくなるおそれや、バルブがバルブシートに衝撃的に着座して異音を生じるおそれがある。
As wear of the adjusting screw's protruding end and arm recess progresses, the coefficient of friction between the adjusting screw's protruding end and arm recess decreases, so the adjust screw can easily rotate and move in the pushing direction during engine operation. Become. In this case, since the swing fulcrum of the arm is shifted, the valve lift amount may be reduced, or the valve may be shockedly seated on the valve seat to generate noise.
また、アジャストスクリュの雄ねじとハウジングの雌ねじの間の潤滑も、アームにはねかけられるエンジンオイルで行なわれるが、上記の動弁装置においては、ハウジングの上端面がシリンダヘッドの上面よりも上方に突出した配置となっており、アームにはねかけられたエンジンオイルがハウジングとアジャストスクリュの間に入り込みにくい。そのため、アジャストスクリュの雄ねじとハウジングの雌ねじの間の潤滑が悪く、雄ねじと雌ねじの焼き付きや摩耗を生じやすかった。
In addition, lubrication between the male screw of the adjusting screw and the female screw of the housing is also performed by engine oil splashed on the arm. However, in the valve operating device described above, the upper end surface of the housing is located above the upper surface of the cylinder head. The projecting arrangement makes it difficult for engine oil splashed on the arm to enter between the housing and the adjusting screw. Therefore, the lubrication between the male screw of the adjusting screw and the female screw of the housing is poor, and the male screw and the female screw are likely to be seized and worn.
アジャストスクリュの雄ねじとハウジングの雌ねじの摩耗が進行すると、雄ねじと雌ねじの間の摩擦係数が低下するので、エンジン作動中、アジャストスクリュが回転して押し込み方向に移動しやすくなる。この場合、アームの揺動支点がずれるので、バルブリフト量が小さくなるおそれや、バルブがバルブシートに衝撃的に着座して異音を生じるおそれがある。
As the wear of the male screw of the adjustment screw and the female screw of the housing progresses, the friction coefficient between the male screw and the female screw decreases, so that the adjustment screw rotates and easily moves in the pushing direction during engine operation. In this case, since the swing fulcrum of the arm is shifted, the valve lift amount may be reduced, or the valve may be shockedly seated on the valve seat to generate noise.
この発明が解決しようとする課題は、アジャストスクリュの回転抵抗が、アジャストスクリュの突出端の摩耗や、アームの凹部の摩耗や、雄ねじと雌ねじの摩耗によって低下するのを防止することである。
The problem to be solved by the present invention is to prevent the rotational resistance of the adjustment screw from being reduced by wear of the protruding end of the adjustment screw, wear of the recess of the arm, or wear of the male screw and the female screw.
上記の課題を解決するため、前記アームを上下に貫通する通油孔を設け、その通油孔の下端を前記アームの凹部内に開口させ、その通油孔を通じて前記アームの凹部内にエンジンオイルを導入するようにした。このようにすると、アームにはねかけられたエンジンオイルが通油孔を通って凹部内に導入されるので、アジャストスクリュの突出端とアームの凹部の間の潤滑性が向上し、アジャストスクリュの突出端とアームの凹部が摩耗しにくくなる。
In order to solve the above-described problem, an oil passage hole is provided that penetrates the arm up and down, and a lower end of the oil passage hole is opened in the recess of the arm, and the engine oil enters the recess of the arm through the oil passage hole. Was introduced. In this way, the engine oil splashed on the arm is introduced into the recess through the oil passage hole, so that the lubricity between the protruding end of the adjustment screw and the recess of the arm is improved, and the adjustment screw The protruding end and the arm recess are less likely to wear.
このアーム式動弁装置は、次の構成を加えることができる。
1)前記アームの凹部の曲率中心と前記アジャストスクリュの突出端の曲率中心とを互いにオフセットすることにより、アジャストスクリュの突出端に楔効果をもたせる。
2)前記アジャストスクリュの突出端の中央に凹面または平坦面を形成し、その凹面または平坦面の直径を、アジャストスクリュの突出端の直径の半分よりも大きくする。
3)前記アジャストスクリュの突出端の表面を、表面粗さがRa0.4以上の梨地とする。
4)前記アームの凹部の内面を、表面粗さがRa0.4以上の梨地とする。
5)前記アジャストスクリュの突出端の表面に油膜排除溝を形成する。
6)前記アームの凹部の内面に油膜排除溝を形成する。 This arm type valve gear can add the following structure.
1) By offsetting the center of curvature of the recess of the arm and the center of curvature of the protruding end of the adjusting screw, the protruding end of the adjusting screw has a wedge effect.
2) A concave surface or a flat surface is formed at the center of the protruding end of the adjusting screw, and the diameter of the concave surface or the flat surface is larger than half of the diameter of the protruding end of the adjusting screw.
3) The surface of the protruding end of the adjusting screw is a matte surface having a surface roughness Ra of 0.4 or more.
4) The inner surface of the concave portion of the arm is a satin surface having a surface roughness Ra of 0.4 or more.
5) An oil film exclusion groove is formed on the surface of the protruding end of the adjustment screw.
6) An oil film removal groove is formed on the inner surface of the recess of the arm.
1)前記アームの凹部の曲率中心と前記アジャストスクリュの突出端の曲率中心とを互いにオフセットすることにより、アジャストスクリュの突出端に楔効果をもたせる。
2)前記アジャストスクリュの突出端の中央に凹面または平坦面を形成し、その凹面または平坦面の直径を、アジャストスクリュの突出端の直径の半分よりも大きくする。
3)前記アジャストスクリュの突出端の表面を、表面粗さがRa0.4以上の梨地とする。
4)前記アームの凹部の内面を、表面粗さがRa0.4以上の梨地とする。
5)前記アジャストスクリュの突出端の表面に油膜排除溝を形成する。
6)前記アームの凹部の内面に油膜排除溝を形成する。 This arm type valve gear can add the following structure.
1) By offsetting the center of curvature of the recess of the arm and the center of curvature of the protruding end of the adjusting screw, the protruding end of the adjusting screw has a wedge effect.
2) A concave surface or a flat surface is formed at the center of the protruding end of the adjusting screw, and the diameter of the concave surface or the flat surface is larger than half of the diameter of the protruding end of the adjusting screw.
3) The surface of the protruding end of the adjusting screw is a matte surface having a surface roughness Ra of 0.4 or more.
4) The inner surface of the concave portion of the arm is a satin surface having a surface roughness Ra of 0.4 or more.
5) An oil film exclusion groove is formed on the surface of the protruding end of the adjustment screw.
6) An oil film removal groove is formed on the inner surface of the recess of the arm.
上記1)の構成を加えたアーム式動弁装置として、例えば、次の構成のものを挙げることができる。前記アームの凹部は、前記アジャストスクリュの軸心を含む平面に沿った断面形状が円弧形状であり、その凹部の円弧中心は、凹部の円弧半径がアジャストスクリュの軸心と交わるようにアジャストスクリュの軸心からオフセットした位置に配置され、前記アジャストスクリュの突出端は、アジャストスクリュの軸心を含む平面に沿った断面形状が、アジャストスクリュの軸心上に中心を有する円弧形状であり、その突出端の円弧半径は、前記アームの凹部の円弧半径よりも小さい。
As an arm type valve gear to which the configuration of 1) above is added, for example, the following configuration can be cited. The recess of the arm has an arc shape in cross section along the plane including the axis of the adjustment screw, and the center of the arc of the recess is such that the arc radius of the recess intersects with the axis of the adjustment screw. The protruding end of the adjusting screw is arranged at a position offset from the axis, and the cross-sectional shape along the plane including the axis of the adjusting screw is an arc shape having a center on the axis of the adjusting screw. The arc radius of the end is smaller than the arc radius of the recess of the arm.
上記3)4)で言う梨地とは、方向性のない均一な凹凸からなる面のことである。
The satin mentioned in 3) and 4) above is a surface composed of uniform unevenness without directionality.
上記5)の構成を加える場合、油膜排除溝は、周方向に延びるように形成してもよく、螺旋状に延びるように形成してもよい。これらの油膜排除溝の形成は、切削によって行なってもよいが、転造により行なうと、アジャストスクリュの突出端の強度が高まり、耐久性が向上する。
When the configuration 5) above is added, the oil film removal groove may be formed so as to extend in the circumferential direction or may be formed so as to extend in a spiral shape. The formation of these oil film exclusion grooves may be performed by cutting, but if the rolling is performed by rolling, the strength of the protruding end of the adjusting screw is increased and the durability is improved.
また、油膜排除溝は、軸方向に延びるように形成してもよい。この油膜排除溝は、周方向に間隔をおいて複数形成すると、アジャストスクリュの回転角によらずに安定した油膜排除効果を発揮させることができる。この油膜排除溝の形成は、鍛造により行なうと、アジャストスクリュの突出端の強度が高まり、耐久性が向上する。
Further, the oil film exclusion groove may be formed so as to extend in the axial direction. If a plurality of the oil film removal grooves are formed at intervals in the circumferential direction, a stable oil film removal effect can be exhibited regardless of the rotation angle of the adjusting screw. When the oil film exclusion groove is formed by forging, the strength of the protruding end of the adjusting screw is increased and the durability is improved.
また、上記の課題を解決するため、前記ハウジングの上端面を、前記シリンダヘッドの上面よりも下方に配置し、そのハウジングの上端面に、アームにはねかけられたエンジンオイルが溜まるようにすることができる。このようにすると、ハウジングの上端面に溜まったエンジンオイルが、アジャストスクリュの雄ねじとハウジングの雌ねじの間に入り込むので、アジャストスクリュの雄ねじとハウジングの雌ねじの間の潤滑性が向上し、雄ねじと雌ねじが摩耗しにくくなる。
In order to solve the above problem, the upper end surface of the housing is disposed below the upper surface of the cylinder head so that the engine oil splashed on the arm accumulates on the upper end surface of the housing. be able to. In this case, the engine oil accumulated on the upper end surface of the housing enters between the male screw of the adjusting screw and the female screw of the housing, so that the lubricity between the male screw of the adjusting screw and the female screw of the housing is improved, and the male screw and the female screw are improved. Is less likely to wear.
前記ハウジングの上端面を、前記シリンダヘッドの上面よりも下方に配置する場合、前記シリンダヘッドの上面に、前記収容穴を囲む環状凹部を設けることができる。この場合、さらに次の構成を加えることができる。
1)前記環状凹部の内面を、環状凹部内に溜まったエンジンオイルを前記収容穴に導くテーパ状の傾斜面とする。
2)前記シリンダヘッドの上面に、前記環状凹部を囲む筒状の突起を設ける。 When the upper end surface of the housing is disposed below the upper surface of the cylinder head, an annular recess surrounding the accommodation hole can be provided on the upper surface of the cylinder head. In this case, the following configuration can be further added.
1) The inner surface of the annular recess is a tapered inclined surface that guides the engine oil accumulated in the annular recess to the accommodation hole.
2) A cylindrical protrusion surrounding the annular recess is provided on the upper surface of the cylinder head.
1)前記環状凹部の内面を、環状凹部内に溜まったエンジンオイルを前記収容穴に導くテーパ状の傾斜面とする。
2)前記シリンダヘッドの上面に、前記環状凹部を囲む筒状の突起を設ける。 When the upper end surface of the housing is disposed below the upper surface of the cylinder head, an annular recess surrounding the accommodation hole can be provided on the upper surface of the cylinder head. In this case, the following configuration can be further added.
1) The inner surface of the annular recess is a tapered inclined surface that guides the engine oil accumulated in the annular recess to the accommodation hole.
2) A cylindrical protrusion surrounding the annular recess is provided on the upper surface of the cylinder head.
また、前記ハウジングの上端面を、前記シリンダヘッドの上面よりも下方に配置する場合、次の構成を加えることができる。
1)前記ハウジングの上端面を、ハウジングの上端面に溜まったエンジンオイルを内径側に導くテーパ状の傾斜面とする。
2)前記ハウジングの底部を上下に貫通する貫通孔を設け、前記収容穴の底面に、前記貫通孔と連通する排油孔を設ける。 Moreover, when arrange | positioning the upper end surface of the said housing below the upper surface of the said cylinder head, the following structure can be added.
1) The upper end surface of the housing is a tapered inclined surface that guides engine oil accumulated on the upper end surface of the housing to the inner diameter side.
2) A through hole that vertically penetrates the bottom of the housing is provided, and an oil drain hole that communicates with the through hole is provided on the bottom surface of the accommodation hole.
1)前記ハウジングの上端面を、ハウジングの上端面に溜まったエンジンオイルを内径側に導くテーパ状の傾斜面とする。
2)前記ハウジングの底部を上下に貫通する貫通孔を設け、前記収容穴の底面に、前記貫通孔と連通する排油孔を設ける。 Moreover, when arrange | positioning the upper end surface of the said housing below the upper surface of the said cylinder head, the following structure can be added.
1) The upper end surface of the housing is a tapered inclined surface that guides engine oil accumulated on the upper end surface of the housing to the inner diameter side.
2) A through hole that vertically penetrates the bottom of the housing is provided, and an oil drain hole that communicates with the through hole is provided on the bottom surface of the accommodation hole.
この発明は、ハウジングから突出する方向の軸方向力をアジャストスクリュに付与する圧縮コイルばねを前記リターンスプリングとして用いたアーム式動弁装置に適用することができ、この場合、前記雄ねじと雌ねじは鋸歯ねじを採用することができる。
The present invention can be applied to an arm type valve gear that uses a compression coil spring that applies an axial force in a direction protruding from a housing to an adjustment screw as the return spring. In this case, the male screw and the female screw are serrated. Screws can be employed.
また、この発明は、ハウジングから突出する方向の回転力をアジャストスクリュに付与するねじりばねを前記リターンスプリングとして用いたアーム式動弁装置にも適用することができ、この場合、前記雄ねじと雌ねじは鋸歯ねじ、三角ねじ、または台形ねじを採用することができる。ねじりばねとしては、例えば、ねじりコイルばね、ゼンマイばね、竹の子ばねが挙げられる。
The present invention can also be applied to an arm type valve gear that uses a torsion spring that applies a rotational force in a direction protruding from a housing to an adjustment screw as the return spring. In this case, the male screw and the female screw are Sawtooth screws, triangular screws, or trapezoidal screws can be employed. Examples of the torsion spring include a torsion coil spring, a spring, and a bamboo spring.
前記アジャストスクリュは、前記ハウジング内に軸方向にスライド可能に挿入されたピボット部材と、そのピボット部材のハウジングへの挿入端を支持し、前記雄ねじを外周に有する雄ねじ部材と、前記ピボット部材と雄ねじ部材の間に挟まれた弾性部材とで構成することができる。
The adjustment screw includes a pivot member inserted in the housing so as to be slidable in the axial direction, a male screw member supporting an insertion end of the pivot member into the housing, and having the male screw on an outer periphery, and the pivot member and the male screw. It can be comprised with the elastic member pinched | interposed between the members.
この場合、前記ピボット部材のハウジング内への挿入端に角穴を形成し、その角穴に嵌合する角軸を前記雄ねじ部材に形成し、その角軸と前記角穴の嵌合によって前記ピボット部材と雄ねじ部材が一体に回転するようにすると好ましい。このようにすると、ピボット部材の回転操作により雄ねじ部材を回転させることができるので、雄ねじ部材をハウジング内に組み付ける作業が容易である。
In this case, a square hole is formed at the insertion end of the pivot member into the housing, a square shaft that fits into the square hole is formed in the male screw member, and the pivot is formed by fitting the square shaft and the square hole. It is preferable that the member and the male screw member rotate together. If it does in this way, since a male screw member can be rotated by rotation operation of a pivot member, the operation | work which assembles a male screw member in a housing is easy.
この発明のアーム式動弁装置は、アームにはねかけられたエンジンオイルを凹部内に導入する通油孔を設けたので、アジャストスクリュの突出端とアームの凹部の間の潤滑が良く、アジャストスクリュの突出端とアームの凹部が摩耗しにくい。そのため、アジャストスクリュの突出端とアームの凹部の間の摩擦係数が低下しにくく、アジャストスクリュの回転抵抗が低下しにくい。
In the arm type valve operating apparatus according to the present invention, since the oil passage hole for introducing the engine oil splashed into the recess is provided in the arm, the lubrication between the protruding end of the adjustment screw and the recess of the arm is good. The protruding end of the screw and the recess of the arm are less likely to wear. Therefore, the coefficient of friction between the protruding end of the adjusting screw and the recess of the arm is unlikely to decrease, and the rotational resistance of the adjusting screw is unlikely to decrease.
また、前記アジャストスクリュの軸心を含む平面に沿った断面での前記アームの凹部の曲率半径を、アジャストスクリュの突出端の曲率半径よりも大きくし、前記アームの凹部の曲率中心と前記アジャストスクリュの突出端の曲率中心とを互いにオフセットすることにより、アジャストスクリュの突出端に楔効果をもたせたものは、アームの凹部でアジャストスクリュの突出端を押圧したときに、アジャストスクリュの突出端が、その楔効果によってアームの凹部に食い込むように嵌合する。そのため、突出端と凹部との間に大きい摩擦抵抗が生じ、エンジンオイルとしてFMオイルを用いた場合にも、アジャストスクリュの突出端とアームの凹部との間の摩擦抵抗を確保することができる。
Further, the curvature radius of the recess of the arm in a cross section along the plane including the axis of the adjustment screw is made larger than the curvature radius of the protruding end of the adjustment screw, and the curvature center of the recess of the arm and the adjustment screw are adjusted. By offsetting the center of curvature of the projecting end of each other, the projecting end of the adjusting screw has a wedge effect.When the projecting end of the adjusting screw is pressed by the recess of the arm, the projecting end of the adjusting screw The wedge effect fits into the recess of the arm. Therefore, a large frictional resistance is generated between the protruding end and the concave portion, and even when FM oil is used as the engine oil, the frictional resistance between the protruding end of the adjusting screw and the concave portion of the arm can be ensured.
また、前記アジャストスクリュの突出端の中央に凹面または平坦面を形成し、その凹面または平坦面の直径を、アジャストスクリュの突出端の直径の半分よりも大きくしたものは、アジャストスクリュの突出端とアームの凹部とが外径側で接触するので、アジャストスクリュの突出端とアームの凹部との間の摩擦抵抗が大きく、エンジンオイルとしてFMオイルを用いた場合にも、アジャストスクリュの突出端とアームの凹部との間の摩擦抵抗を確保することができる。
Further, a concave surface or a flat surface is formed in the center of the protruding end of the adjusting screw, and the diameter of the concave surface or the flat surface is larger than half the diameter of the protruding end of the adjusting screw. Since the arm recess comes into contact with the outer diameter side, the frictional resistance between the protruding end of the adjusting screw and the recess of the arm is large. Even when FM oil is used as the engine oil, the protruding end of the adjusting screw and the arm It is possible to ensure a frictional resistance between the concave portion and the concave portion.
また、前記アジャストスクリュの突出端の表面を、表面粗さがRa0.4以上の梨地としたものは、アームからアジャストスクリュに押し込み方向の荷重が負荷されたときに、アームの凹部とアジャストスクリュの突出端の間に存在するエンジンオイルが梨地の凹凸の隙間内に逃げるので、アームの凹部とアジャストスクリュの突出端の間に、スクイズ効果による油膜が形成されにくい。そのため、エンジンオイルの粘性が高い低温時においても、アジャストスクリュの突出端とアームの凹部との間の摩擦抵抗を確保することができる。
Further, the surface of the protruding end of the adjusting screw that has a matte surface with a surface roughness of Ra 0.4 or more is provided with a concave portion of the arm and the adjusting screw when a load in the pushing direction is applied from the arm to the adjusting screw. Since the engine oil existing between the projecting ends escapes into the gap between the irregularities of the satin finish, it is difficult to form an oil film due to the squeeze effect between the recesses of the arm and the projecting ends of the adjustment screw. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
また、前記アームの凹部の内面を、表面粗さがRa0.4以上の梨地としたものも、アームからアジャストスクリュに押し込み方向の荷重が負荷されたときに、アームの凹部とアジャストスクリュの突出端の間に存在するエンジンオイルが梨地の凹凸の隙間内に逃げるので、アームの凹部とアジャストスクリュの突出端の間に、スクイズ効果による油膜が形成されにくい。そのため、エンジンオイルの粘性が高い低温時においても、アジャストスクリュの突出端とアームの凹部との間の摩擦抵抗を確保することができる。
In addition, the inner surface of the recess of the arm having a satin finish with a surface roughness of Ra 0.4 or more can be applied to the recess of the arm and the protruding end of the adjustment screw when a load in the pushing direction is applied from the arm to the adjustment screw. Since the engine oil existing between them escapes into the gaps between the uneven surfaces of the matte surface, it is difficult to form an oil film due to the squeeze effect between the recesses of the arms and the protruding ends of the adjustment screws. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
また、前記アジャストスクリュの突出端の表面に油膜排除溝を形成したものは、アームからアジャストスクリュに押し込み方向の荷重が負荷されたときに、アームの凹部とアジャストスクリュの突出端の間に存在するエンジンオイルが油膜排除溝内に逃げるので、アームの凹部とアジャストスクリュの突出端の間に、スクイズ効果による油膜が形成されにくい。そのため、エンジンオイルの粘性が高い低温時においても、アジャストスクリュの突出端とアームの凹部との間の摩擦抵抗を確保することができる。
In addition, the oil screw exclusion groove formed on the surface of the protruding end of the adjusting screw exists between the recess of the arm and the protruding end of the adjusting screw when a load in the pushing direction is applied from the arm to the adjusting screw. Since the engine oil escapes into the oil film exclusion groove, an oil film due to the squeeze effect is hardly formed between the recess of the arm and the protruding end of the adjustment screw. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
また、前記アームの凹部の内面に油膜排除溝を形成したものも、アームからアジャストスクリュに押し込み方向の荷重が負荷されたときに、アームの凹部とアジャストスクリュの突出端の間に存在するエンジンオイルが油膜排除溝内に逃げるので、アームの凹部とアジャストスクリュの突出端の間に、スクイズ効果による油膜が形成されにくい。そのため、エンジンオイルの粘性が高い低温時においても、アジャストスクリュの突出端とアームの凹部との間の摩擦抵抗を確保することができる。
In addition, an oil film exclusion groove formed on the inner surface of the recess of the arm also has engine oil that exists between the recess of the arm and the protruding end of the adjustment screw when a load in the pushing direction is applied from the arm to the adjustment screw. Since it escapes into the oil film removal groove, an oil film due to the squeeze effect is hardly formed between the recess of the arm and the protruding end of the adjustment screw. Therefore, even at a low temperature when the viscosity of the engine oil is high, it is possible to ensure a frictional resistance between the protruding end of the adjusting screw and the recess of the arm.
また、前記ハウジングの上端面を、前記シリンダヘッドの上面よりも下方に配置し、そのハウジングの上端面に、前記アームにはねかけられたエンジンオイルが溜まるようにしたものは、ハウジングの上端面に溜まったエンジンオイルが、アジャストスクリュの雄ねじとハウジングの雌ねじの間に入り込むので、アジャストスクリュの雄ねじとハウジングの雌ねじの間の潤滑が良く、雄ねじと雌ねじの焼き付きや摩耗を生じにくい。そのため、雄ねじと雌ねじの間の摩擦係数が低下しにくく、アジャストスクリュの回転抵抗が低下しにくい。
Further, the upper end surface of the housing is disposed below the upper surface of the cylinder head, and engine oil splashed on the arm is accumulated on the upper end surface of the housing. Since the engine oil collected in the screw enters between the male screw of the adjusting screw and the female screw of the housing, the lubricating between the male screw of the adjusting screw and the female screw of the housing is good, and seizure and wear of the male screw and the female screw are unlikely to occur. Therefore, the coefficient of friction between the male screw and the female screw is unlikely to decrease, and the rotational resistance of the adjusting screw is unlikely to decrease.
また、前記シリンダヘッドの上面に、前記収容穴を囲む環状凹部を設けたものは、その環状凹部内にもエンジンオイルが溜まるので、ハウジングの上方に溜まるエンジンオイルの量が多い。そのため、アームにはねかけられるエンジンオイルが少ないときにも、アジャストスクリュの雄ねじとハウジングの雌ねじの間を安定して潤滑することができる。
Further, when the cylinder head is provided with an annular recess surrounding the accommodation hole on the upper surface of the cylinder head, the engine oil also accumulates in the annular recess, so that a large amount of engine oil accumulates above the housing. Therefore, even when the engine oil splashed on the arm is small, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
また、前記環状凹部の内面をテーパ状の傾斜面としたものは、その環状凹部の内面の傾斜によって環状凹部内のエンジンオイルが収容穴に向かって流れるので、環状凹部内に溜まったエンジンオイルの量が少なくなったときにも、アジャストスクリュの雄ねじとハウジングの雌ねじの間を安定して潤滑することができる。
Further, in the case where the inner surface of the annular recess has a tapered inclined surface, the engine oil in the annular recess flows toward the accommodation hole due to the inclination of the inner surface of the annular recess. Even when the amount is reduced, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
さらに、前記シリンダヘッドの上面に、前記環状凹部を囲む筒状の突起を設けたものは、その筒状の突起内の空間にもエンジンオイルを溜めることができるので、ハウジングの上方に溜まるエンジンオイルの量がより多い。そのため、アームにはねかけられるエンジンオイルが少ないときにも、アジャストスクリュの雄ねじとハウジングの雌ねじの間を安定して潤滑することができる。
Furthermore, when the cylinder head is provided with a cylindrical protrusion on the upper surface of the cylinder head, the engine oil can be stored in the space in the cylindrical protrusion, so that the engine oil is stored above the housing. The amount of more. Therefore, even when the engine oil splashed on the arm is small, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
また、前記ハウジングの上端面をテーパ状の傾斜面としたものは、その上端面の傾斜によってハウジングの上端面に溜まったエンジンオイルが内径側に流れるので、ハウジングの上端面に溜まったエンジンオイルの量が少なくなったときにも、アジャストスクリュの雄ねじとハウジングの雌ねじの間を安定して潤滑することができる。
Further, in the case where the upper end surface of the housing has a tapered inclined surface, the engine oil accumulated on the upper end surface of the housing flows to the inner diameter side due to the inclination of the upper end surface, so the engine oil accumulated on the upper end surface of the housing Even when the amount is reduced, the space between the male screw of the adjusting screw and the female screw of the housing can be stably lubricated.
また、前記ハウジングの底部を上下に貫通する貫通孔を設け、前記収容穴の底面に、前記貫通孔と連通する排油孔を設けたものは、アジャストスクリュの雄ねじとハウジングの雌ねじの間を通ってハウジング内に流れ込んだエンジンオイルが、前記貫通孔と排油孔を介してハウジングから排出される。そのため、エンジンオイルに混入したコンタミや摩耗粉が、アジャストスクリュの雄ねじとハウジングの雌ねじの間に滞留しにくく、雄ねじと雌ねじが摩耗しにくい。
In addition, a through hole that vertically penetrates the bottom of the housing and an oil drain hole that communicates with the through hole on the bottom surface of the housing hole passes between the male screw of the adjusting screw and the female screw of the housing. Then, the engine oil flowing into the housing is discharged from the housing through the through hole and the oil drain hole. For this reason, the contamination and wear powder mixed in the engine oil are unlikely to stay between the male screw of the adjusting screw and the female screw of the housing, and the male screw and the female screw are not easily worn.
1 シリンダヘッド
1a 上面
6 アーム
11 収容穴
12 ハウジング
12a 上端面
13 雌ねじ
14 雄ねじ
15 アジャストスクリュ
15A ピボット部材
15B 雄ねじ部材
15C ばね座金
17 リターンスプリング
21 突出端
22 凹部
24 平坦面
25 通油孔
26 貫通孔
27 排油孔
28 凹面
29,30 油膜排除溝
31 環状凹部
32 突起
35 角穴
36 角軸
D1 アジャストスクリュの突出端の直径
D2 平坦面の直径
D3 凹面の直径
O1 アジャストスクリュの突出端の円弧中心
O2 凹部の円弧中心
A1 アジャストスクリュの突出端の円弧半径
A2 凹部の円弧半径
L アジャストスクリュの軸心 DESCRIPTION OFSYMBOLS 1 Cylinder head 1a Upper surface 6 Arm 11 Accommodating hole 12 Housing 12a Upper end surface 13 Female screw 14 Male screw 15 Adjust screw 15A Pivot member 15B Male screw member 15C Spring washer 17 Return spring 21 Protruding end 22 Recess 24 Flat surface 25 Oil passage hole 26 Through hole 27 Oil drain hole 28 Concave surface 29, 30 Oil film exclusion groove 31 Annular recess 32 Projection 35 Square hole 36 Square axis D 1 Diameter of projecting end of adjusting screw D 2 Diameter of flat surface D 3 Diameter of concave surface O 1 Diameter of projecting end of adjusting screw Arc center O 2 Arc center of the recess A 1 Arc radius A of the protruding end of the adjusting screw A 2 Arc radius L of the recess The axis of the adjusting screw
1a 上面
6 アーム
11 収容穴
12 ハウジング
12a 上端面
13 雌ねじ
14 雄ねじ
15 アジャストスクリュ
15A ピボット部材
15B 雄ねじ部材
15C ばね座金
17 リターンスプリング
21 突出端
22 凹部
24 平坦面
25 通油孔
26 貫通孔
27 排油孔
28 凹面
29,30 油膜排除溝
31 環状凹部
32 突起
35 角穴
36 角軸
D1 アジャストスクリュの突出端の直径
D2 平坦面の直径
D3 凹面の直径
O1 アジャストスクリュの突出端の円弧中心
O2 凹部の円弧中心
A1 アジャストスクリュの突出端の円弧半径
A2 凹部の円弧半径
L アジャストスクリュの軸心 DESCRIPTION OF
図1に、この発明の第1実施形態のアーム式動弁装置を示す。この動弁装置は、エンジンのシリンダヘッド1の吸気ポート2に設けられたバルブ3と、そのバルブ3に接続されたバルブステム4と、カム5の回転に応じて揺動するアーム6と、ラッシュアジャスタ7とを有する。
FIG. 1 shows an arm type valve operating apparatus according to a first embodiment of the present invention. This valve operating apparatus includes a valve 3 provided in an intake port 2 of a cylinder head 1 of an engine, a valve stem 4 connected to the valve 3, an arm 6 that swings according to rotation of a cam 5, a lash And an adjuster 7.
バルブステム4は、バルブ3から上方に延び、シリンダヘッド1を摺動可能に貫通している。バルブステム4の上部外周には、環状のスプリングリテーナ8が固定され、スプリングリテーナ8の下面とシリンダヘッド1の上面の間にバルブスプリング9が組み込まれている。バルブスプリング9は、スプリングリテーナ8を介してバルブステム4を上方に付勢し、その付勢力によってバルブ3をバルブシート10に着座させている。
The valve stem 4 extends upward from the valve 3 and slidably penetrates the cylinder head 1. An annular spring retainer 8 is fixed to the upper outer periphery of the valve stem 4, and a valve spring 9 is incorporated between the lower surface of the spring retainer 8 and the upper surface of the cylinder head 1. The valve spring 9 urges the valve stem 4 upward via the spring retainer 8, and the valve 3 is seated on the valve seat 10 by the urging force.
図2に示すように、ラッシュアジャスタ7は、シリンダヘッド1の上面1aに開口した収容穴11に挿入される筒状のハウジング12と、ハウジング12の内周に形成された雌ねじ13にねじ係合する雄ねじ14を下部外周に有するアジャストスクリュ15と、ハウジング12の下端に固定された底部材16と、アジャストスクリュ15と底部材16の間に組み込まれたリターンスプリング17とからなる。
As shown in FIG. 2, the lash adjuster 7 is screw-engaged with a cylindrical housing 12 inserted into a receiving hole 11 opened in the upper surface 1 a of the cylinder head 1 and a female screw 13 formed on the inner periphery of the housing 12. An adjustment screw 15 having a male screw 14 on the outer periphery of the lower part, a bottom member 16 fixed to the lower end of the housing 12, and a return spring 17 incorporated between the adjustment screw 15 and the bottom member 16.
雄ねじ14と雌ねじ13は、軸線に沿った断面形状が非対称形状の鋸歯状に形成されており、アジャストスクリュ15をハウジング12に押し込む方向の荷重が負荷されたときに圧力を受ける圧力側フランク18のフランク角が、遊び側フランク19のフランク角よりも大きくなっている。
The male screw 14 and the female screw 13 are formed in a sawtooth shape having an asymmetric cross section along the axis, and the pressure-side flank 18 that receives pressure when a load in the direction of pushing the adjusting screw 15 into the housing 12 is applied. The flank angle is larger than the flank angle of the play side flank 19.
リターンスプリング17は圧縮コイルばねである。リターンスプリング17は、下端が底部材16で支持され、上端がスプリングシート20を介してハウジング12から突出する方向の軸方向力をアジャストスクリュ15に付与している。その軸方向力によって、アジャストスクリュ15は、ハウジング12から上方に突出する方向に付勢されている。
The return spring 17 is a compression coil spring. The return spring 17 has a lower end supported by the bottom member 16 and an upper end that applies an axial force in a direction protruding from the housing 12 via the spring seat 20 to the adjusting screw 15. Due to the axial force, the adjusting screw 15 is biased in a direction protruding upward from the housing 12.
図1に示すように、アーム6は、一方の端部下面に、アジャストスクリュ15のハウジング12からの突出端21に嵌合する凹部22を有し、アジャストスクリュ15の突出端21を中心として揺動可能に支持されている。また、アーム6の他方の端部下面は、バルブステム4の上端に接触し、アーム6の中央部には、アーム6の上方に配置されたカム5に接触するローラ23が取り付けられている。
As shown in FIG. 1, the arm 6 has a recess 22 that fits into the protruding end 21 of the adjusting screw 15 from the housing 12 on the lower surface of one end, and swings around the protruding end 21 of the adjusting screw 15. It is supported movably. The lower surface of the other end of the arm 6 is in contact with the upper end of the valve stem 4, and a roller 23 that is in contact with the cam 5 disposed above the arm 6 is attached to the center of the arm 6.
図2に示すように、アジャストスクリュ15の突出端21と、アーム6の凹部22は、いずれも半球状に形成されており、アジャストスクリュ15の突出端21は、アーム6の凹部22の内面に接触している。また、アジャストスクリュ15の突出端21の中央には平坦面24が設けられている。平坦面24の直径D2は、突出端21の直径D1の半分よりも大きい。
As shown in FIG. 2, the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 are both formed in a hemispherical shape, and the protruding end 21 of the adjusting screw 15 is formed on the inner surface of the recessed portion 22 of the arm 6. In contact. A flat surface 24 is provided at the center of the protruding end 21 of the adjusting screw 15. The diameter D 2 of the flat surface 24 is larger than half of the diameter D 1 of the protruding end 21.
アーム6には、アーム6の端部を上下に貫通する通油孔25が形成されている。通油孔25の下端は、アーム6の凹部22内に開口しており、その通油孔25を通じて、アーム6にはねかけられたエンジンオイルを凹部22内に導入するようになっている。
The arm 6 has an oil passage hole 25 penetrating the end of the arm 6 up and down. The lower end of the oil passage hole 25 opens into the recess 22 of the arm 6, and engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25.
ハウジング12の上端面12aから底部材16の下端面16aまでの長さは、収容穴11の長さ(シリンダヘッド1の上面1aから収容穴11の底までの長さ)よりも短い。そのため、ハウジング12の上端面12aが、シリンダヘッド1の上面1aよりも下方に奥まった配置となっており、アーム6にはねかけられたエンジンオイルが、ハウジング12の上端面12aに溜まるようになっている。
The length from the upper end surface 12a of the housing 12 to the lower end surface 16a of the bottom member 16 is shorter than the length of the accommodation hole 11 (the length from the upper surface 1a of the cylinder head 1 to the bottom of the accommodation hole 11). For this reason, the upper end surface 12a of the housing 12 is arranged so as to be recessed below the upper surface 1a of the cylinder head 1 so that the engine oil splashed on the arm 6 accumulates on the upper end surface 12a of the housing 12. It has become.
底部材16には、上下に貫通する貫通孔26が形成されており、収容穴11の底面には、貫通孔26と連通する排油孔27が形成されている。そのため、ハウジング12の上端面12aから雄ねじ14と雌ねじ13の隙間を通ってハウジング12内に流れ込んだエンジンオイルは、貫通孔26と排油孔27とを順に通ってハウジング12から排出される。
The bottom member 16 has a through hole 26 penetrating vertically, and an oil drain hole 27 communicating with the through hole 26 is formed on the bottom surface of the accommodation hole 11. Therefore, the engine oil that has flowed into the housing 12 from the upper end surface 12a of the housing 12 through the gap between the male screw 14 and the female screw 13 is discharged from the housing 12 through the through hole 26 and the oil draining hole 27 in order.
次に、このアーム式動弁装置の動作例を説明する。
Next, an operation example of this arm type valve gear will be described.
エンジンの作動によりカム5が回転して、カム5のカム山部5aがアーム6を押し下げると、バルブ3がバルブシート10から離れて、吸気ポート2を開く。このとき、アジャストスクリュ15に押し込み方向の荷重が負荷されるが、アジャストスクリュ15の雄ねじ14とハウジング12の雌ねじ13の間の摩擦抵抗と、アジャストスクリュ15の突出端21とアーム6の凹部22の間の摩擦抵抗とによってアジャストスクリュ15の回転が防止され、その結果、アジャストスクリュ15の軸方向位置が固定される。
When the cam 5 is rotated by the operation of the engine and the cam crest 5a of the cam 5 pushes down the arm 6, the valve 3 is separated from the valve seat 10 and the intake port 2 is opened. At this time, although the load in the pushing direction is applied to the adjusting screw 15, the friction resistance between the male screw 14 of the adjusting screw 15 and the female screw 13 of the housing 12, the protruding end 21 of the adjusting screw 15, and the recess 22 of the arm 6 The rotation of the adjusting screw 15 is prevented by the frictional resistance therebetween, and as a result, the axial position of the adjusting screw 15 is fixed.
さらに、カム5が回転して、カム山部5aがローラ23の位置を過ぎると、バルブスプリング9の付勢力によってバルブステム4が上昇し、バルブ3がバルブシート10に着座して、吸気ポート2を閉じる。
Further, when the cam 5 rotates and the cam crest 5a passes the position of the roller 23, the valve stem 4 is raised by the urging force of the valve spring 9, the valve 3 is seated on the valve seat 10, and the intake port 2 Close.
また、エンジン作動中に、シリンダヘッド1、バルブステム4、アーム6など、動弁装置の構成部材間に熱膨張差が生じ、カム5とアーム6の間の距離が大きくなったときは、リターンスプリング17の付勢力によってアジャストスクリュ15が回転しながら突出方向に移動するので、カム5のベースサークル5bとローラ23の間に隙間が生じない。
In addition, when the difference in thermal expansion occurs between the components of the valve operating device such as the cylinder head 1, the valve stem 4, and the arm 6 during engine operation, and the distance between the cam 5 and the arm 6 increases, the return Since the adjusting screw 15 moves in the protruding direction while rotating by the urging force of the spring 17, there is no gap between the base circle 5 b of the cam 5 and the roller 23.
反対に、バルブ3とバルブシート10の接触面が摩耗したときは、カム5のベースサークル5bがローラ23の位置にあるときにも、バルブスプリング9の付勢力がアジャストスクリュ15に押し込み荷重としてかかり続けるため、カム山部5aがローラ23の位置を通過する時に生じる雄ねじ14と雌ねじ13の間で生じる微小な滑りが累積され、アジャストスクリュ15が押し込み方向に徐々に移動する。その結果、バルブステム4が上昇するので、バルブ3とバルブシート10の接触面間に隙間が生じない。
On the other hand, when the contact surface between the valve 3 and the valve seat 10 is worn, the urging force of the valve spring 9 is applied to the adjusting screw 15 as a pressing load even when the base circle 5b of the cam 5 is at the position of the roller 23. In order to continue, the minute slip which arises between the external thread 14 and the internal thread 13 which arises when the cam crest part 5a passes the position of the roller 23 is accumulated, and the adjusting screw 15 gradually moves in the pushing direction. As a result, the valve stem 4 is raised, so that no gap is generated between the contact surfaces of the valve 3 and the valve seat 10.
このアーム式動弁装置は、アーム6にはねかけられたエンジンオイルを、通油孔25を通じて凹部22内に導入するので、アジャストスクリュ15の突出端21とアーム6の凹部22の間の潤滑が良く、アジャストスクリュ15の突出端21とアーム6の凹部22の摩耗が進行しにくい。そのため、アジャストスクリュ15の突出端21とアーム6の凹部22の間の摩擦係数が低下しにくく、アジャストスクリュ15の回転抵抗が低下しにくい。
In this arm type valve operating apparatus, engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25, so that lubrication between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 is performed. And the wear of the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 does not easily progress. Therefore, the coefficient of friction between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 is difficult to decrease, and the rotational resistance of the adjusting screw 15 is difficult to decrease.
また、このアーム式動弁装置は、アジャストスクリュ15の突出端21の中央に平坦面24が形成されているので、アジャストスクリュ15の突出端21とアーム6の凹部22とが、外径側で接触する。そのため、アジャストスクリュ15の突出端21とアーム6の凹部22との間の摩擦抵抗が大きく、エンジンオイルとして、有機モリブデン入りのエンジンオイル(以下、「FMオイル」と言う)を用いた場合にも、アジャストスクリュ15の突出端21とアーム6の凹部22との間の摩擦抵抗を確保することができる。ここで、有機モリブデンとしては、モリブデンジチオカーバメイト(MoDTC)やモリブデンジチオフォスフェート(MoDTP)が挙げられる。
Moreover, since this arm type valve operating apparatus has the flat surface 24 formed in the center of the protrusion end 21 of the adjustment screw 15, the protrusion end 21 of the adjustment screw 15 and the recessed part 22 of the arm 6 are outside diameter side. Contact. For this reason, the friction resistance between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 is large, and even when engine oil containing organic molybdenum (hereinafter referred to as “FM oil”) is used as engine oil. The frictional resistance between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 can be ensured. Here, examples of the organic molybdenum include molybdenum dithiocarbamate (MoDTC) and molybdenum dithiophosphate (MoDTP).
また、このアーム式動弁装置は、アーム6やシリンダヘッド1にはねかけられたエンジンオイルがハウジング12の上端面12aに溜まるので、雄ねじ14と雌ねじ13の間にエンジンオイルが入り込みやすい。そのため、雄ねじ14と雌ねじ13の間の潤滑が良く、雄ねじ14と雌ねじ13の焼き付きや摩耗を生じにくい。
Further, in this arm type valve operating apparatus, the engine oil splashed on the arm 6 and the cylinder head 1 accumulates on the upper end surface 12a of the housing 12, so that the engine oil easily enters between the male screw 14 and the female screw 13. Therefore, lubrication between the male screw 14 and the female screw 13 is good, and seizure and wear of the male screw 14 and the female screw 13 are difficult to occur.
また、このアーム式動弁装置は、雄ねじ14と雌ねじ13の間を通ってハウジング12内に流れ込んだエンジンオイルが、貫通孔26と排油孔27を介してハウジング12から排出される。そのため、エンジンオイルに混入したコンタミや摩耗粉が雄ねじ14と雌ねじ13の間に滞留しにくく、雄ねじ14と雌ねじ13が摩耗しにくい。
Further, in this arm type valve operating apparatus, the engine oil that has flowed into the housing 12 through between the male screw 14 and the female screw 13 is discharged from the housing 12 through the through hole 26 and the oil draining hole 27. Therefore, the contamination and wear powder mixed in the engine oil are less likely to stay between the male screw 14 and the female screw 13, and the male screw 14 and the female screw 13 are less likely to wear.
この実施形態では、アジャストスクリュ15の突出端21の中央に平坦面24を形成したが、平坦面24にかえて、図3に示すように、突出端21の直径D1の半分よりも大きい直径D3の凹面28を形成してもよい。このようにしても、アジャストスクリュ15の突出端21とアーム6の凹部22とが、外径側で接触するので、アジャストスクリュ15の突出端21とアーム6の凹部22との間の摩擦抵抗が大きく、アジャストスクリュ15の回転を効果的に防止することができる。また、エンジンオイルが凹面28に溜まるので、アジャストスクリュ15の突出端21とアーム6の凹部22との間の潤滑耐久性を向上させることができる。
In this embodiment, to form a flat surface 24 at the center of the protruding end 21 of the adjusting screw 15, instead of the flat surface 24, as shown in FIG. 3, larger in diameter than half the diameter D 1 of the projecting end 21 it may form a D 3 of the concave 28. Even in this case, the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 are in contact with each other on the outer diameter side, so that the frictional resistance between the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 is reduced. The rotation of the adjusting screw 15 can be effectively prevented. Further, since the engine oil accumulates in the concave surface 28, the durability of lubrication between the protruding end 21 of the adjusting screw 15 and the concave portion 22 of the arm 6 can be improved.
次に、この発明の第2実施形態のアーム式動弁装置を説明する。第1実施形態に対応する部分は、同一の符号を付して説明を省略する。
Next, an arm type valve gear according to a second embodiment of the present invention will be described. Portions corresponding to the first embodiment are denoted by the same reference numerals and description thereof is omitted.
図4に示すように、アジャストスクリュ15の突出端21は、アジャストスクリュ15の軸心Lを含む平面に沿った断面形状が、軸心L上に中心O1を有する円弧形状となるように形成されている。アーム6の凹部22も、アジャストスクリュ15の軸心Lを含む平面に沿った断面形状が円弧形状であり、凹部22の円弧中心O2は、凹部22の円弧半径A2が軸心Lと交わるように軸心Lからオフセットした位置に配置されている。突出端21の円弧半径A1は、凹部22の円弧半径A2よりも小さい。
As shown in FIG. 4, the protruding end 21 of the adjusting screw 15 is formed such that a cross-sectional shape along a plane including the axis L of the adjusting screw 15 has an arc shape having a center O 1 on the axis L. Has been. The recess 22 of the arm 6 also has an arc shape in cross section along the plane including the axis L of the adjusting screw 15, and the arc center O 2 of the recess 22 intersects with the axis L of the arc radius A 2 of the recess 22. Thus, it is arranged at a position offset from the axis L. The arc radius A 1 of the protruding end 21 is smaller than the arc radius A 2 of the recess 22.
このように、凹部22の曲率中心(円弧中心O2)と突出端21の曲率中心(円弧中心O1)が互いにオフセットしているので、アーム6の凹部22でアジャストスクリュ15の突出端21を押圧したとき、突出端21に楔効果が生じ、その楔効果によって突出端21は凹部22に食い込むように嵌合する。
Thus, since the center of curvature of the recess 22 (arc center O 2 ) and the center of curvature of the projecting end 21 (arc center O 1 ) are offset from each other, the projecting end 21 of the adjusting screw 15 is moved by the recess 22 of the arm 6. When pressed, a wedge effect is generated at the protruding end 21, and the protruding end 21 fits into the recess 22 by the wedge effect.
このアーム式動弁装置は、第1実施形態と同様、アーム6にはねかけられたエンジンオイルを、通油孔25を通じて凹部22内に導入するので、アジャストスクリュ15の突出端21とアーム6の凹部22の間の潤滑が良い。そのため、アジャストスクリュ15の突出端21とアーム6の凹部22の摩耗が進行しにくく、アジャストスクリュ15の突出端21とアーム6の凹部22の間の摩擦係数が低下しにくい。
In this arm type valve operating apparatus, engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25 as in the first embodiment, so that the protruding end 21 of the adjusting screw 15 and the arm 6 Lubrication between the recesses 22 is good. Therefore, the wear of the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 does not easily progress, and the friction coefficient between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 is unlikely to decrease.
また、このアーム式動弁装置は、アーム6の凹部22でアジャストスクリュ15の突出端21を押圧したときに、突出端21が、その楔効果によって凹部22に食い込むように嵌合する。そのため、突出端21と凹部22との間に大きい摩擦抵抗が生じ、エンジンオイルとしてFMオイルを用いた場合にも、アジャストスクリュ15の突出端21とアーム6の凹部22との間の摩擦抵抗を確保することができる。
Further, this arm type valve gear is fitted so that the protruding end 21 bites into the recessed portion 22 by the wedge effect when the protruding end 21 of the adjusting screw 15 is pressed by the recessed portion 22 of the arm 6. Therefore, a large frictional resistance is generated between the protruding end 21 and the recessed portion 22, and even when FM oil is used as the engine oil, the frictional resistance between the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 is reduced. Can be secured.
このアーム式動弁装置は、雄ねじ14と雌ねじ13の噛み合い長さを短く設定すると、雄ねじ14と雌ねじ13の圧力側フランク18に作用する面圧が高くなり、その圧力側フランク18の摩耗によって雄ねじ14と雌ねじ13の間の摩擦抵抗が低下しやすくなるが、突出端21と凹部22の間の摩擦抵抗が大きいので、エンジン作動中、アジャストスクリュ15は押し込み方向に過剰に移動することがない。そのため、このアーム式動弁装置は、凹部22の曲率中心O2と突出端21の曲率中心O1とをオフセットしないアーム式動弁装置と比較して、アジャストスクリュ15とハウジング12の軸方向長さを抑えることができ、軽量化が可能である。
In this arm type valve operating apparatus, when the meshing length of the male screw 14 and the female screw 13 is set short, the surface pressure acting on the pressure side flank 18 of the male screw 14 and the female screw 13 is increased, and the male screw is worn by the wear of the pressure side flank 18. Although the frictional resistance between the screw 14 and the female screw 13 tends to decrease, the frictional resistance between the protruding end 21 and the recess 22 is large, so that the adjusting screw 15 does not move excessively in the pushing direction during engine operation. Therefore, this arm type valve operating device is longer in the axial direction of the adjusting screw 15 and the housing 12 than an arm type valve operating device in which the center of curvature O 2 of the recess 22 and the center of curvature O 1 of the protruding end 21 are not offset. Therefore, the weight can be reduced.
次に、この発明の第3実施形態のアーム式動弁装置を説明する。第1実施形態に対応する部分は、同一の符号を付して説明を省略する。
Next, an arm type valve gear according to a third embodiment of the present invention will be described. Portions corresponding to the first embodiment are denoted by the same reference numerals and description thereof is omitted.
図5に示すように、アジャストスクリュ15の突出端21の表面は、ショットピーニングを施すことによって表面粗さがRa0.4以上の梨地となっている。この梨地は、鋭角粒のメディアを使用したショットピーニングで形成することができ、また、アジャストスクリュ15に熱処理(例えば、浸炭処理や窒化処理)を施す場合は、その熱処理前にショットピーニングを施すことによって形成することができる。表面粗さRaは、JIS B0601(製品の幾何特性仕様(GPS)-表面性状:輪郭曲線方式-用語,定義及び表面性状パラメータ)による。
As shown in FIG. 5, the surface of the protruding end 21 of the adjusting screw 15 is a satin finish having a surface roughness of Ra 0.4 or more by performing shot peening. This satin can be formed by shot peening using sharp-angled media, and when the adjustment screw 15 is subjected to heat treatment (for example, carburizing or nitriding), the shot peening is performed before the heat treatment. Can be formed. The surface roughness Ra is in accordance with JIS B0601 (product geometric characteristic specification (GPS) -surface property: contour curve method-terminology, definition and surface property parameter).
このアーム式動弁装置は、アーム6からアジャストスクリュ15に押し込み方向の荷重が負荷されたときに、アーム6の凹部22とアジャストスクリュ15の突出端21の間に存在するエンジンオイルが梨地の凹凸の隙間内に逃げるので、アーム6の凹部22とアジャストスクリュ15の突出端21の間に、スクイズ効果による油膜が形成されにくい。そのため、エンジンオイルの粘性が高い低温時においても、アジャストスクリュ15の突出端21とアーム6の凹部22との間の摩擦抵抗を確保することができる。
In this arm type valve operating apparatus, when a load in the pushing direction is applied from the arm 6 to the adjusting screw 15, the engine oil existing between the recessed portion 22 of the arm 6 and the protruding end 21 of the adjusting screw 15 is uneven. Therefore, it is difficult to form an oil film due to the squeeze effect between the recess 22 of the arm 6 and the protruding end 21 of the adjustment screw 15. Therefore, the frictional resistance between the projecting end 21 of the adjusting screw 15 and the recess 22 of the arm 6 can be ensured even at low temperatures when the viscosity of the engine oil is high.
また、このアーム式動弁装置は、雄ねじ14と雌ねじ13の噛み合い長さを短く設定すると、雄ねじ14と雌ねじ13の圧力側フランク18に作用する面圧が高くなり、その圧力側フランク18の摩耗によって雄ねじ14と雌ねじ13の間の摩擦抵抗が低下しやすくなるが、突出端21と凹部22の間の摩擦抵抗が確保されているので、エンジン作動中、アジャストスクリュ15は押し込み方向に過剰に移動することがない。そのため、このアーム式動弁装置は、アジャストスクリュの突出端の表面が滑らかなアーム式動弁装置と比較して、アジャストスクリュ15とハウジング12の軸方向長さを抑えることができ、軽量化が可能である。
Further, in this arm type valve operating apparatus, when the meshing length of the male screw 14 and the female screw 13 is set short, the surface pressure acting on the pressure side flank 18 of the male screw 14 and the female screw 13 is increased, and the wear of the pressure side flank 18 is increased. As a result, the frictional resistance between the male screw 14 and the female screw 13 tends to decrease, but since the frictional resistance between the protruding end 21 and the recess 22 is ensured, the adjustment screw 15 moves excessively in the pushing direction during engine operation. There is nothing to do. Therefore, this arm type valve operating device can suppress the axial length of the adjusting screw 15 and the housing 12 as compared with the arm type valve operating device in which the surface of the protruding end of the adjusting screw is smooth. Is possible.
アジャストスクリュ15の突出端21の表面を、表面粗さがRa0.4以上の梨地としたときに、アジャストスクリュ15の回転抵抗が確保されることを確認するため、突出端21の表面粗さRaが異なる7本のアジャストスクリュ15を準備し、そのアジャストスクリュ15を組み込んだ各ラッシュアジャスタについて、バルブリフト量(バルブ3の移動ストローク)の安定性を試験したところ、表1に示す結果を得た。表1から、突出端21の表面粗さRaが0.4以上、25以下の範囲にあるものは、バルブリフト量の安定性に優れており、突出端21の表面粗さRaが0.4未満の範囲にあるものよりも、アジャストスクリュ15が押し込み方向に移動しにくくなっていることが分かる。
In order to confirm that the rotational resistance of the adjusting screw 15 is ensured when the surface of the protruding end 21 of the adjusting screw 15 is a matte surface having a surface roughness of Ra 0.4 or more, the surface roughness Ra of the protruding end 21 is ensured. Were prepared, and the stability of the valve lift amount (movement stroke of the valve 3) was tested for each lash adjuster incorporating the adjustment screw 15, and the results shown in Table 1 were obtained. . From Table 1, when the surface roughness Ra of the protruding end 21 is in the range of 0.4 or more and 25 or less, the stability of the valve lift amount is excellent, and the surface roughness Ra of the protruding end 21 is 0.4. It can be seen that the adjustment screw 15 is less likely to move in the push-in direction than in the range below the lower limit.
この実施形態では、アジャストスクリュ15の突出端21の表面を、表面粗さがRa0.4以上の梨地としたが、図9に示すように、アーム6の凹部22の内面にショットピーニングを施すことにより、凹部22の内面を表面粗さがRa0.4以上の梨地としてもよい。このようにしても、アーム6の凹部22とアジャストスクリュ15の突出端21の間に、スクイズ効果による油膜が形成されにくくなり、アジャストスクリュ15の突出端21とアーム6の凹部22との間の摩擦抵抗を確保することができる。
In this embodiment, the surface of the protruding end 21 of the adjusting screw 15 is a matte surface having a surface roughness Ra of 0.4 or more. However, as shown in FIG. 9, shot peening is applied to the inner surface of the recess 22 of the arm 6. Thus, the inner surface of the recess 22 may be a satin having a surface roughness Ra of 0.4 or more. Even in this case, it is difficult to form an oil film due to the squeeze effect between the recessed portion 22 of the arm 6 and the protruding end 21 of the adjusting screw 15, and the gap between the protruding end 21 of the adjusting screw 15 and the recessed portion 22 of the arm 6 is reduced. Frictional resistance can be ensured.
次に、この発明の第4実施形態のアーム式動弁装置を説明する。第1実施形態に対応する部分は、同一の符号を付して説明を省略する。
Next, an arm type valve gear according to a fourth embodiment of the present invention will be described. Portions corresponding to the first embodiment are denoted by the same reference numerals and description thereof is omitted.
図6に示すように、突出端21の表面には、周方向に延びる油膜排除溝29が軸方向に間隔をおいて複数形成されている。
As shown in FIG. 6, a plurality of oil film exclusion grooves 29 extending in the circumferential direction are formed on the surface of the projecting end 21 at intervals in the axial direction.
このアーム式動弁装置は、第1実施形態と同様、アーム6にはねかけられたエンジンオイルが、通油孔25を通じて凹部22内に導入されるので、アジャストスクリュ15の突出端21とアーム6の凹部22の間の潤滑が良い。そのため、アジャストスクリュ15の突出端21とアーム6の凹部22の摩耗が進行しにくく、アジャストスクリュ15の突出端21とアーム6の凹部22の間の摩擦係数が低下しにくい。
In this arm type valve operating apparatus, the engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25 as in the first embodiment, so that the projecting end 21 of the adjustment screw 15 and the arm The lubrication between the six recesses 22 is good. Therefore, the wear of the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 does not easily progress, and the friction coefficient between the protruding end 21 of the adjusting screw 15 and the recess 22 of the arm 6 is unlikely to decrease.
また、このアーム式動弁装置は、アーム6からアジャストスクリュ15に押し込み方向の荷重が負荷されたときに、アーム6の凹部22とアジャストスクリュ15の突出端21の間に存在するエンジンオイルが油膜排除溝29内に逃げるので、アーム6の凹部22とアジャストスクリュ15の突出端21の間に、スクイズ効果による油膜が形成されにくい。そのため、エンジンオイルの粘性が高い低温時においても、アジャストスクリュ15の突出端21とアーム6の凹部22との間の摩擦抵抗を確保することができる。
Further, in this arm type valve operating apparatus, when a load in the pushing direction is applied from the arm 6 to the adjusting screw 15, the engine oil existing between the recessed portion 22 of the arm 6 and the protruding end 21 of the adjusting screw 15 is oil film. Since it escapes into the exclusion groove 29, it is difficult to form an oil film due to the squeeze effect between the recess 22 of the arm 6 and the protruding end 21 of the adjustment screw 15. Therefore, the frictional resistance between the projecting end 21 of the adjusting screw 15 and the recess 22 of the arm 6 can be ensured even at low temperatures when the viscosity of the engine oil is high.
図7に示すように、アジャストスクリュ15の突出端21の油膜排除溝29は、螺旋状に延びるように形成してもよい。このようにしても、アーム6の凹部22とアジャストスクリュ15の突出端21の間に存在するエンジンオイルが油膜排除溝29内に逃げるので、スクイズ効果による油膜を防止することができる。螺旋状に延びる油膜排除溝29は、その下端が凹部22の外側に露出するように形成すると、油膜排除溝29内のエンジンオイルが油膜排除溝29の下端から排出されるので、油膜排除効果が高くなる。
As shown in FIG. 7, the oil film removal groove 29 at the protruding end 21 of the adjustment screw 15 may be formed to extend in a spiral shape. Even in this case, the engine oil existing between the recess 22 of the arm 6 and the protruding end 21 of the adjustment screw 15 escapes into the oil film removal groove 29, so that an oil film due to the squeeze effect can be prevented. When the oil film exclusion groove 29 extending in a spiral shape is formed so that the lower end thereof is exposed to the outside of the recess 22, the engine oil in the oil film exclusion groove 29 is discharged from the lower end of the oil film exclusion groove 29. Get higher.
上述した油膜排除溝29の形成は、切削によって行なってもよいが、転造により行なうと、アジャストスクリュ15の突出端21の強度が高まり、突出端21の耐久性を向上させることができる。
The formation of the oil film exclusion groove 29 described above may be performed by cutting, but if it is performed by rolling, the strength of the protruding end 21 of the adjusting screw 15 is increased, and the durability of the protruding end 21 can be improved.
また、図8に示すように、油膜排除溝29は、軸方向に延びるように形成してもよい。この場合、軸方向に延びる油膜排除溝29は、周方向に間隔をおいて複数形成すると、アジャストスクリュ15の回転角によらずに安定した油膜排除効果を発揮させることができる。軸方向に延びる油膜排除溝29の形成は、切削によって行なってもよいが、鍛造により行なうと、アジャストスクリュ15の突出端21の強度が高まり、耐久性を向上させることができる。
Further, as shown in FIG. 8, the oil film exclusion groove 29 may be formed to extend in the axial direction. In this case, if a plurality of oil film removal grooves 29 extending in the axial direction are formed at intervals in the circumferential direction, a stable oil film removal effect can be exhibited regardless of the rotation angle of the adjustment screw 15. The oil film exclusion groove 29 extending in the axial direction may be formed by cutting. However, if forging is performed, the strength of the protruding end 21 of the adjusting screw 15 is increased, and the durability can be improved.
また、上記実施形態では、アジャストスクリュ15の突出端21の表面に油膜排除溝29を形成したが、図10~図12に示すように、アーム6の凹部22の内面に油膜排除溝30を形成してもよい。このようにしても、アーム6の凹部22とアジャストスクリュ15の突出端21の間に存在するエンジンオイルが油膜排除溝30内に逃げるので、スクイズ効果による油膜を防止することができる。この油膜排除溝30は、例えば、図10に示すように、アーム6の凹部22の内面に周方向に延びるように形成してもよく、図11に示すように、アーム6の凹部22の内面に螺旋状に延びるように形成してもよく、図12に示すように、アーム6の凹部22の内面に軸方向に延びるように形成してもよい。
In the above embodiment, the oil film removal groove 29 is formed on the surface of the protruding end 21 of the adjustment screw 15. However, as shown in FIGS. 10 to 12, the oil film removal groove 30 is formed on the inner surface of the recess 22 of the arm 6. May be. Even in this case, the engine oil existing between the recess 22 of the arm 6 and the projecting end 21 of the adjustment screw 15 escapes into the oil film removal groove 30, so that an oil film due to the squeeze effect can be prevented. For example, as shown in FIG. 10, the oil film removal groove 30 may be formed to extend in the circumferential direction on the inner surface of the recess 22 of the arm 6, and as shown in FIG. 11, the inner surface of the recess 22 of the arm 6. 12 may be formed so as to extend in a spiral shape, or may be formed so as to extend in the axial direction on the inner surface of the recess 22 of the arm 6 as shown in FIG.
シリンダヘッド1の上面1aは、図2に示すように平坦に形成すると、シリンダヘッド1の加工コストを抑えることができるが、図13に示すように、シリンダヘッド1の上面1aに環状の段差を形成することにより、収容穴11を囲む環状凹部31を設けてもよい。このようにすると、その環状凹部31内にもエンジンオイルが溜まるので、ハウジング12の上方に溜まるエンジンオイルの量が多くなる。そのため、アーム6にはねかけられるエンジンオイルが少ないときにも、雄ねじ14と雌ねじ13の間を安定して潤滑することができる。
If the upper surface 1a of the cylinder head 1 is formed flat as shown in FIG. 2, the processing cost of the cylinder head 1 can be reduced. However, as shown in FIG. 13, an annular step is formed on the upper surface 1a of the cylinder head 1. By forming, an annular recess 31 surrounding the accommodation hole 11 may be provided. As a result, the engine oil also accumulates in the annular recess 31, so that the amount of engine oil that accumulates above the housing 12 increases. Therefore, even when the engine oil splashed on the arm 6 is small, the space between the male screw 14 and the female screw 13 can be stably lubricated.
シリンダヘッド1の上面1aに収容穴11を囲む環状凹部31を設ける場合、図14に示すように、その環状凹部31の内面を、環状凹部31内に溜まったエンジンオイルを収容穴11に導くテーパ状の傾斜面としてもよい。このようにすると、環状凹部31の内面の傾斜によって環状凹部31内のエンジンオイルが収容穴11に向かって流れるので、環状凹部31内に溜まったエンジンオイルの量が少なくなったときにも、雄ねじ14と雌ねじ13の間を安定して潤滑することができる。また、収容穴11にハウジング12を挿入するときに、環状凹部31の内面でハウジング12が収容穴11に案内されるので、動弁装置の組立作業が容易である。
When the annular recess 31 surrounding the accommodation hole 11 is provided on the upper surface 1 a of the cylinder head 1, as shown in FIG. 14, the inner surface of the annular recess 31 is tapered to guide the engine oil accumulated in the annular recess 31 to the accommodation hole 11. It is good also as a shape-like inclined surface. In this way, since the engine oil in the annular recess 31 flows toward the accommodation hole 11 due to the inclination of the inner surface of the annular recess 31, the male screw is provided even when the amount of engine oil accumulated in the annular recess 31 decreases. 14 and the internal thread 13 can be stably lubricated. Further, when the housing 12 is inserted into the accommodation hole 11, the housing 12 is guided to the accommodation hole 11 on the inner surface of the annular recess 31, so that the assembly operation of the valve operating device is easy.
また、図15に示すように、シリンダヘッド1の上面1aに、環状凹部31を囲む筒状の突起32を設けてもよい。このようにすると、その筒状の突起32内の空間にもエンジンオイルを溜めることができるので、ハウジング12の上方に溜まるエンジンオイルの量がより多くなる。そのため、シリンダヘッド1にはねかけられるエンジンオイルが少ないときにも、雄ねじ14と雌ねじ13の間を安定して潤滑することができる。
Further, as shown in FIG. 15, a cylindrical protrusion 32 surrounding the annular recess 31 may be provided on the upper surface 1 a of the cylinder head 1. In this way, the engine oil can be stored in the space in the cylindrical projection 32, so that the amount of the engine oil stored above the housing 12 is increased. Therefore, even when the engine oil splashed on the cylinder head 1 is small, the space between the male screw 14 and the female screw 13 can be stably lubricated.
同様に、図13に示すシリンダヘッド1の上面1aにも、環状凹部31を囲む筒状の突起(図示せず)を設けることができる。
Similarly, a cylindrical projection (not shown) surrounding the annular recess 31 can be provided on the upper surface 1a of the cylinder head 1 shown in FIG.
また、図16に示すように、ハウジング12の上端面12aを、ハウジング12の上端面12aに溜まったエンジンオイルを内径側に導くテーパ状の傾斜面とすると好ましい。このようにすると、上端面12aの傾斜によってハウジング12の上端面12aに溜まったエンジンオイルが内径側に流れるので、ハウジング12の上端面12aに溜まったエンジンオイルの量が少なくなったときにも、雄ねじ14と雌ねじ13の間を安定して潤滑することができる。
Further, as shown in FIG. 16, it is preferable that the upper end surface 12a of the housing 12 is a tapered inclined surface that guides engine oil accumulated on the upper end surface 12a of the housing 12 to the inner diameter side. In this way, since the engine oil collected on the upper end surface 12a of the housing 12 flows to the inner diameter side due to the inclination of the upper end surface 12a, even when the amount of engine oil collected on the upper end surface 12a of the housing 12 decreases, The space between the male screw 14 and the female screw 13 can be stably lubricated.
同様に、図12、図13に示すハウジング12の上端面12aも、ハウジング12の上端面12aに溜まったエンジンオイルを内径側に導くテーパ状の傾斜面としてもよい。
Similarly, the upper end surface 12a of the housing 12 shown in FIGS. 12 and 13 may be a tapered inclined surface that guides engine oil accumulated on the upper end surface 12a of the housing 12 to the inner diameter side.
上記環状凹部31は、シリンダヘッド1を切削して形成してもよいが、シリンダヘッド1のアルミダイカストにより型成形すると、低コストである。
The annular recess 31 may be formed by cutting the cylinder head 1. However, when the die is formed by aluminum die casting of the cylinder head 1, the cost is low.
第1実施形態では、アジャストスクリュ15をハウジング12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17として圧縮コイルばねを採用したが、図17に示すように、ねじりコイルばねを採用してもよい。
In the first embodiment, a compression coil spring is used as the return spring 17 that urges the adjustment screw 15 in a direction protruding upward from the housing 12, but a torsion coil spring may be used as shown in FIG. .
図17において、リターンスプリング17は、その下端が、底部材16に形成された係止孔33に係止し、上端が、アジャストスクリュ15に形成された係止孔34に係止しており、そのねじり変形によって、ハウジング12から突出する方向の回転力をアジャストスクリュ15に付与している。
In FIG. 17, the return spring 17 has a lower end locked in a locking hole 33 formed in the bottom member 16, and an upper end locked in a locking hole 34 formed in the adjusting screw 15. Due to the torsional deformation, rotational force in a direction protruding from the housing 12 is applied to the adjusting screw 15.
リターンスプリング17としては、ねじりコイルばね以外のねじりばね(例えば、ゼンマイばねや竹の子ばね)を採用してもよい。第2~第4実施形態においても同様に、リターンスプリング17としてねじりコイルばねを採用することができる。
As the return spring 17, a torsion spring (for example, a spring spring or a bamboo spring) other than the torsion coil spring may be employed. Similarly, in the second to fourth embodiments, a torsion coil spring can be employed as the return spring 17.
リターンスプリング17としてねじりばねを採用する場合、アジャストスクリュ15の外周の雄ねじ14と、ハウジング12の内周の雌ねじ13は、図18に示すように、上下対称の三角ねじを採用してもよく、図19に示すように、上下対称の台形ねじを採用してもよい。
When a torsion spring is employed as the return spring 17, the male screw 14 on the outer periphery of the adjustment screw 15 and the female screw 13 on the inner periphery of the housing 12 may employ vertically symmetrical triangular screws as shown in FIG. As shown in FIG. 19, a vertically symmetrical trapezoidal screw may be employed.
次に、この発明の第5実施形態のアーム式動弁装置を説明する。第1実施形態に対応する部分は、同一の符号を付して説明を省略する。
Next, an arm type valve gear according to a fifth embodiment of the present invention will be described. Portions corresponding to the first embodiment are denoted by the same reference numerals and description thereof is omitted.
図20に示すように、アジャストスクリュ15は、ハウジング12内に軸方向にスライド可能に挿入されたピボット部材15Aと、そのピボット部材15Aのハウジング12への挿入端を支持し、雄ねじ14を外周に有する雄ねじ部材15Bと、ピボット部材15Aと雄ねじ部材15Bの間に挟まれたばね座金15Cとからなる。ばね座金15Cとしては、例えば、皿ばね座金や波形座金などを用いることができる。
As shown in FIG. 20, the adjusting screw 15 supports a pivot member 15A inserted into the housing 12 so as to be slidable in the axial direction, an insertion end of the pivot member 15A into the housing 12, and a male screw 14 on the outer periphery. And a spring washer 15C sandwiched between the pivot member 15A and the male screw member 15B. As the spring washer 15C, for example, a disc spring washer or a corrugated washer can be used.
ピボット部材15Aは、ハウジング12内への挿入端の中央に角穴35が形成されている。雄ねじ部材15Bには、角穴35に嵌合する角軸36が形成されており、ピボット部材15Aを回転操作したときに、角軸36と角穴35の嵌合によってピボット部材15Aと雄ねじ部材15Bが一体に回転するようになっている。
The pivot member 15A has a square hole 35 formed at the center of the insertion end into the housing 12. The male screw member 15B is formed with a square shaft 36 that fits into the square hole 35. When the pivot member 15A is rotated, the pivot member 15A and the male screw member 15B are fitted by fitting the square shaft 36 and the square hole 35. Are designed to rotate together.
リターンスプリング17はねじりコイルばねである。リターンスプリング17は、その下端が、底部材16に形成された係止孔33に係止し、上端が、雄ねじ部材15Bに形成された係止孔34に係止しており、そのねじり変形によって、ピボット部材15Aがハウジング12から突出する方向の回転力を雄ねじ部材15Bに付与している。
The return spring 17 is a torsion coil spring. The return spring 17 has a lower end locked in a locking hole 33 formed in the bottom member 16, and an upper end locked in a locking hole 34 formed in the male screw member 15B. The rotational force in the direction in which the pivot member 15A protrudes from the housing 12 is applied to the male screw member 15B.
このアーム式動弁装置は、第1実施形態と同様、アーム6にはねかけられたエンジンオイルが、アーム6に形成された通油孔25を通じて凹部22内に導入されるので、ピボット部材15Aのハウジング12からの突出端21とアーム6の凹部22の間の潤滑が良く、突出端21と凹部22の摩耗が進行しにくい。その他の効果も、第1実施形態と同様である。
In this arm type valve operating apparatus, the engine oil splashed on the arm 6 is introduced into the recess 22 through the oil passage hole 25 formed in the arm 6 as in the first embodiment. Lubrication between the projecting end 21 from the housing 12 and the recess 22 of the arm 6 is good, and wear of the projecting end 21 and the recess 22 does not easily progress. Other effects are the same as those of the first embodiment.
また、このアーム式動弁装置は、エンジンが高温の状態で停止し、その後、エンジンが冷却して動弁装置の構成部材間に収縮差が生じたときに、雄ねじ部材15Bとピボット部材15Aの間のばね座金15Cが圧縮することにより、その収縮差が吸収される。そのため、エンジンの再始動時に、動弁装置の構成部材間の収縮差による隙間がバルブ3とバルブシート10の間に生じず、圧縮漏れが生じない。
In addition, this arm type valve operating system is configured such that when the engine is stopped at a high temperature and thereafter the engine is cooled to cause a contraction difference between the constituent members of the valve operating apparatus, the male screw member 15B and the pivot member 15A When the spring washer 15C in between 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 3 and the valve seat 10, and compression leakage does not occur.
また、このアーム式動弁装置は、角軸36と角穴35の嵌合によってピボット部材15Aと雄ねじ部材15Bが一体に回転するようになっているので、ピボット部材15Aの回転操作により、雄ねじ部材15Bを回転させることができる。そのため、角軸36と角穴35を設けないものと比較して、雄ねじ部材15Bをハウジング12内に組み付ける作業が容易である。
Further, in this arm type valve operating apparatus, the pivot member 15A and the male screw member 15B rotate integrally by fitting the square shaft 36 and the square hole 35. Therefore, the male screw member can be rotated by rotating the pivot member 15A. 15B can be rotated. Therefore, the work of assembling the male screw member 15B in the housing 12 is easier than that in which the square shaft 36 and the square hole 35 are not provided.
この実施形態では、ピボット部材15Aと雄ねじ部材15Bの間に挟む弾性部材としてばね座金15Cを使用したが、ばね座金15Cにかえて他の弾性部材(例えば、圧縮コイルばね)を使用してもよい。
In this embodiment, the spring washer 15C is used as an elastic member sandwiched between the pivot member 15A and the male screw member 15B. However, another elastic member (for example, a compression coil spring) may be used instead of the spring washer 15C. .
リターンスプリング17としてねじりコイルばねを用いる場合、リターンスプリング17は、図20に示すように、円筒状に巻いたものを用いてもよく、図21に示すように、円錐形に巻いたものを用いてもよい。
When a torsion coil spring is used as the return spring 17, the return spring 17 may be a cylinder wound as shown in FIG. 20, or may be a cone wound as shown in FIG. May be.
また、リターンスプリング17としては、図22~図24に示すように、ねじりコイルばね以外のねじりばね(例えば、ゼンマイばねや竹の子ばね)を採用してもよい。
Further, as the return spring 17, as shown in FIGS. 22 to 24, a torsion spring (for example, a spring spring or a bamboo spring) other than the torsion coil spring may be employed.
図22において、リターンスプリング17は、薄板状の素材を渦巻き状に巻いたゼンマイばねである。リターンスプリング17は、その大径端がハウジング12の底部材16に回り止めされ、小径端が、雄ねじ部材15Bのハウジング12内への挿入端の突起37に形成したスリットに差し込まれており、そのねじり変形によって、ピボット部材15Aがハウジング12から突出する方向の回転力を雄ねじ部材15Bに付与している。また、雄ねじ部材15Bの外周の雄ねじ14と、ハウジング12の内周の雌ねじ13は、上下対称の三角ねじである。
Referring to FIG. 22, the return spring 17 is a spring spring in which a thin plate material is wound in a spiral shape. The return spring 17 has a large-diameter end that is prevented from rotating by the bottom member 16 of the housing 12, and a small-diameter end that is inserted into a slit formed in the projection 37 at the insertion end of the male screw member 15B into the housing 12, The rotational force in the direction in which the pivot member 15A protrudes from the housing 12 is applied to the male screw member 15B by torsional deformation. The external thread 14 on the outer periphery of the external thread member 15B and the internal thread 13 on the inner periphery of the housing 12 are vertically symmetrical triangular screws.
図23、図24において、リターンスプリング17は、薄板状の素材を螺旋状に巻いた竹の子ばねである。リターンスプリング17は、その大径端がハウジング12の底部材16に回り止めされ、小径端が、雄ねじ部材15Bのハウジング12内への挿入端の突起38に形成されたスリットに差し込まれており、そのねじり変形によって、ピボット部材15Aがハウジング12から突出する方向の回転力を雄ねじ部材15Bに付与している。また、雄ねじ部材15Bの外周の雄ねじ14と、ハウジング12の内周の雌ねじ13は、上下対称の台形ねじである。
23 and 24, the return spring 17 is a bamboo shoot spring in which a thin plate material is spirally wound. The return spring 17 has a large-diameter end that is prevented from rotating by the bottom member 16 of the housing 12, and a small-diameter end that is inserted into a slit formed in the projection 38 at the insertion end of the male screw member 15B into the housing 12, Due to the torsional deformation, a rotational force in a direction in which the pivot member 15A protrudes from the housing 12 is applied to the male screw member 15B. The external thread 14 on the outer periphery of the external thread member 15B and the internal thread 13 on the inner periphery of the housing 12 are vertically symmetrical trapezoidal screws.
Claims (25)
- シリンダヘッド(1)の上面(1a)に開口した収容穴(11)に挿入される筒状のハウジング(12)と、そのハウジング(12)の内周に形成された雌ねじ(13)にねじ係合する雄ねじ(14)を外周に有するアジャストスクリュ(15)と、そのアジャストスクリュ(15)を前記ハウジング(12)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(17)と、前記アジャストスクリュ(15)のハウジング(12)からの突出端(21)が嵌合する凹部(22)をもつアーム(6)とを有し、前記アジャストスクリュ(15)のハウジング(12)からの突出端(21)が半球状に形成され、その突出端(21)を前記アーム(6)の凹部(22)の内面に接触させたアーム式動弁装置において、
前記アーム(6)を上下に貫通する通油孔(25)を設け、その通油孔(25)の下端を前記アーム(6)の凹部(22)内に開口させ、その通油孔(25)を通じて前記アーム(6)の凹部(22)内にエンジンオイルを導入するようにしたことを特徴とするアーム式動弁装置。 The cylindrical housing (12) to be inserted into the accommodation hole (11) opened in the upper surface (1a) of the cylinder head (1) and the female screw (13) formed on the inner periphery of the housing (12) An adjusting screw (15) having a mating male screw (14) on the outer periphery, a return spring (17) for biasing the adjusting screw (15) in a direction protruding upward from the housing (12), and the adjusting screw ( 15) and an arm (6) having a recess (22) into which a projecting end (21) from the housing (12) is fitted, and the projecting end (21) of the adjusting screw (15) from the housing (12). ) Is formed in a hemispherical shape, and the protruding end (21) is in contact with the inner surface of the recess (22) of the arm (6).
An oil passage hole (25) penetrating the arm (6) vertically is provided, and the lower end of the oil passage hole (25) is opened into the recess (22) of the arm (6). ) Through which the engine oil is introduced into the recess (22) of the arm (6). - 前記アーム(6)の凹部(22)の曲率中心(O2)と前記アジャストスクリュ(15)の突出端(21)の曲率中心(O1)とを互いにオフセットすることにより、アジャストスクリュ(15)の突出端(21)に楔効果をもたせた請求項1に記載のアーム式動弁装置。 By adjusting the curvature center (O 2 ) of the recess (22) of the arm (6) and the curvature center (O 1 ) of the protruding end (21) of the adjustment screw (15), the adjustment screw (15) The arm type valve gear according to claim 1, wherein the protruding end (21) has a wedge effect.
- 前記アーム(6)の凹部(22)は、前記アジャストスクリュ(15)の軸心(L)を含む平面に沿った断面形状が円弧形状であり、その凹部(22)の円弧中心(O2)は、凹部(22)の円弧半径(A2)がアジャストスクリュ(15)の軸心(L)と交わるようにアジャストスクリュ(15)の軸心(L)からオフセットした位置に配置され、前記アジャストスクリュ(15)の突出端(21)は、アジャストスクリュ(15)の軸心(L)を含む平面に沿った断面形状が、アジャストスクリュ(15)の軸心(L)上に中心(O1)を有する円弧形状であり、その突出端(21)の円弧半径(A1)は、前記アーム(6)の凹部(22)の円弧半径(A2)よりも小さい請求項2に記載のアーム式動弁装置。 The recess (22) of the arm (6) has an arc shape in cross section along the plane including the axis (L) of the adjustment screw (15), and the arc center (O 2 ) of the recess (22). Is arranged at a position offset from the axis (L) of the adjustment screw (15) so that the arc radius (A 2 ) of the recess (22) intersects the axis (L) of the adjustment screw (15), and the adjustment The projecting end (21) of the screw (15) has a cross-sectional shape along the plane including the axis (L) of the adjusting screw (15) centered on the axis (L) of the adjusting screw (15) (O 1 3. The arm according to claim 2 , wherein an arc radius (A 1 ) of the protruding end (21) is smaller than an arc radius (A 2 ) of the recess (22) of the arm (6). Valve gear.
- 前記アジャストスクリュ(15)の突出端(21)の中央に凹面(28)または平坦面(24)を形成し、その凹面(28)または平坦面(24)の直径(D3,D2)を、アジャストスクリュ(15)の突出端(21)の直径(D1)の半分よりも大きくしたことを特徴とする請求項1に記載のアーム式動弁装置。 A concave surface (28) or a flat surface (24) is formed at the center of the protruding end (21) of the adjustment screw (15), and the diameter (D 3 , D 2 ) of the concave surface (28) or the flat surface (24) is set. The arm type valve gear according to claim 1, characterized in that it is larger than half of the diameter (D 1 ) of the protruding end (21) of the adjusting screw (15).
- 前記アジャストスクリュ(15)の突出端(21)の表面を、表面粗さがRa0.4以上の梨地とした請求項1に記載のアーム式動弁装置。 The arm type valve gear according to claim 1, wherein the surface of the protruding end (21) of the adjusting screw (15) is a matte surface having a surface roughness of Ra 0.4 or more.
- 前記アーム(6)の凹部(22)の内面を、表面粗さがRa0.4以上の梨地とした請求項1に記載のアーム式動弁装置。 The arm type valve gear according to claim 1, wherein the inner surface of the recess (22) of the arm (6) is a matte surface having a surface roughness of Ra 0.4 or more.
- 前記アジャストスクリュ(15)の突出端(21)の表面に油膜排除溝(29)を形成した請求項1に記載のアーム式動弁装置。 The arm type valve gear according to claim 1, wherein an oil film exclusion groove (29) is formed on the surface of the protruding end (21) of the adjustment screw (15).
- 前記油膜排除溝(29)が、周方向に延びるように形成された請求項7に記載のアーム式動弁装置。 The arm type valve gear according to claim 7, wherein the oil film removal groove (29) is formed to extend in a circumferential direction.
- 前記油膜排除溝(29)が、螺旋状に延びるように形成された請求項7に記載のアーム式動弁装置。 The arm type valve gear according to claim 7, wherein the oil film removal groove (29) is formed to extend in a spiral shape.
- 前記油膜排除溝(29)を転造により形成した請求項8または9に記載のアーム式動弁装置。 The arm type valve gear according to claim 8 or 9, wherein the oil film exclusion groove (29) is formed by rolling.
- 前記油膜排除溝(29)が、軸方向に延びるように形成された請求項7に記載のアーム式動弁装置。 The arm type valve gear according to claim 7, wherein the oil film removal groove (29) is formed to extend in the axial direction.
- 前記油膜排除溝(29)が、周方向に間隔をおいて複数形成された請求項11に記載のアーム式動弁装置。 The arm type valve gear according to claim 11, wherein a plurality of the oil film exclusion grooves (29) are formed at intervals in the circumferential direction.
- 前記油膜排除溝(29)を鍛造により形成した請求項11または12に記載のアーム式動弁装置。 The arm type valve gear according to claim 11 or 12, wherein the oil film exclusion groove (29) is formed by forging.
- 前記アーム(6)の凹部(22)の内面に油膜排除溝(30)を形成した請求項1に記載のアーム式動弁装置。 The arm type valve gear according to claim 1, wherein an oil film exclusion groove (30) is formed on an inner surface of the recess (22) of the arm (6).
- シリンダヘッド(1)の上面(1a)に開口した収容穴(11)に挿入される筒状のハウジング(12)と、そのハウジング(12)の内周に形成された雌ねじ(13)にねじ係合する雄ねじ(14)を外周に有するアジャストスクリュ(15)と、そのアジャストスクリュ(15)を前記ハウジング(12)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(17)と、前記アジャストスクリュ(15)のハウジング(12)からの突出端(21)が嵌合する凹部(22)をもつアーム(6)とを有し、前記アジャストスクリュ(15)のハウジング(12)からの突出端(21)が半球状に形成され、その突出端(21)を前記アーム(6)の凹部(22)の内面に接触させたアーム式動弁装置において、
前記ハウジング(12)の上端面(12a)を、前記シリンダヘッド(1)の上面(1a)よりも下方に配置し、そのハウジング(12)の上端面(12a)に、前記アーム(6)にはねかけられたエンジンオイルが溜まるようにしたことを特徴とするアーム式動弁装置。 The cylindrical housing (12) to be inserted into the accommodation hole (11) opened in the upper surface (1a) of the cylinder head (1) and the female screw (13) formed on the inner periphery of the housing (12) An adjusting screw (15) having a mating male screw (14) on the outer periphery, a return spring (17) for biasing the adjusting screw (15) in a direction protruding upward from the housing (12), and the adjusting screw ( 15) and an arm (6) having a recess (22) into which a projecting end (21) from the housing (12) is fitted, and the projecting end (21) of the adjusting screw (15) from the housing (12). ) Is formed in a hemispherical shape, and the protruding end (21) is in contact with the inner surface of the recess (22) of the arm (6).
The upper end surface (12a) of the housing (12) is disposed below the upper surface (1a) of the cylinder head (1), and the upper end surface (12a) of the housing (12) is connected to the arm (6). An arm type valve operating system characterized in that splashed engine oil is accumulated. - 前記シリンダヘッド(1)の上面(1a)に、前記収容穴(11)を囲む環状凹部(31)を設けた請求項15に記載のアーム式動弁装置。 The arm type valve gear according to claim 15, wherein an annular recess (31) surrounding the accommodation hole (11) is provided on the upper surface (1a) of the cylinder head (1).
- 前記環状凹部(31)の内面を、環状凹部(31)内に溜まったエンジンオイルを前記収容穴(11)に導くテーパ状の傾斜面とした請求項16に記載のアーム式動弁装置。 The arm type valve gear according to claim 16, wherein the inner surface of the annular recess (31) is a tapered inclined surface that guides engine oil accumulated in the annular recess (31) to the accommodation hole (11).
- 前記シリンダヘッド(1)の上面(1a)に、前記環状凹部(31)を囲む筒状の突起(32)を設けた請求項16または17に記載のアーム式動弁装置。 The arm type valve gear according to claim 16 or 17, wherein a cylindrical projection (32) surrounding the annular recess (31) is provided on the upper surface (1a) of the cylinder head (1).
- 前記ハウジング(12)の上端面(12a)を、ハウジング(12)の上端面(12a)に溜まったエンジンオイルを内径側に導くテーパ状の傾斜面とした請求項15から18のいずれかに記載のアーム式動弁装置。 The upper end surface (12a) of the housing (12) is a tapered inclined surface that guides engine oil accumulated on the upper end surface (12a) of the housing (12) to the inner diameter side. Arm type valve gear.
- 前記ハウジング(12)の底部(16)を上下に貫通する貫通孔(26)を設け、前記収容穴(11)の底面に、前記貫通孔(26)と連通する排油孔(27)を設けた請求項15から19のいずれかに記載のアーム式動弁装置。 A through hole (26) that vertically penetrates the bottom (16) of the housing (12) is provided, and an oil drain hole (27) that communicates with the through hole (26) is provided on the bottom surface of the accommodation hole (11). The arm type valve gear according to any one of claims 15 to 19.
- 前記リターンスプリング(17)は、前記ハウジング(12)から突出する方向の軸方向力をアジャストスクリュ(15)に付与する圧縮コイルばねであり、前記雄ねじ(14)と雌ねじ(13)は鋸歯ねじである請求項1から20のいずれかに記載のアーム式動弁装置。 The return spring (17) is a compression coil spring that applies an axial force in a direction protruding from the housing (12) to the adjustment screw (15), and the male screw (14) and the female screw (13) are sawtooth screws. The arm type valve gear according to any one of claims 1 to 20.
- 前記リターンスプリング(17)は、前記ハウジング(12)から突出する方向の回転力をアジャストスクリュ(15)に付与するねじりばねであり、前記雄ねじ(14)と雌ねじ(13)は鋸歯ねじ、三角ねじ、または台形ねじである請求項1から20のいずれかに記載のアーム式動弁装置。 The return spring (17) is a torsion spring that applies a rotational force in a direction protruding from the housing (12) to the adjustment screw (15). The male screw (14) and the female screw (13) are sawtooth screws and triangular screws. The arm type valve gear according to any one of claims 1 to 20, which is a trapezoidal screw.
- 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22に記載のアーム式動弁装置。 The arm type valve gear according to claim 22, wherein the torsion spring is one of a torsion coil spring, a spring, and a bamboo spring.
- 前記アジャストスクリュ(15)が、前記ハウジング(12)内に軸方向にスライド可能に挿入されたピボット部材(15A)と、そのピボット部材(15A)のハウジング(12)内への挿入端を支持し、前記雄ねじ(14)を外周に有する雄ねじ部材(15B)と、前記ピボット部材(15A)と雄ねじ部材(15B)の間に挟まれた弾性部材(15C)とからなる請求項1から23のいずれかに記載のアーム式動弁装置。 The adjustment screw (15) supports a pivot member (15A) inserted into the housing (12) so as to be slidable in the axial direction, and an insertion end of the pivot member (15A) into the housing (12). The male screw member (15B) having the male screw (14) on the outer periphery, and the elastic member (15C) sandwiched between the pivot member (15A) and the male screw member (15B). The arm type valve gear according to claim 1.
- 前記ピボット部材(15A)のハウジング(12)内への挿入端に角穴(35)を形成し、その角穴(35)に嵌合する角軸(36)を前記雄ねじ部材(15B)に形成し、その角軸(36)と前記角穴(35)の嵌合によって前記ピボット部材(15A)と雄ねじ部材(15B)が一体に回転するようにした請求項24に記載のアーム式動弁装置。 A square hole (35) is formed at the insertion end of the pivot member (15A) into the housing (12), and a square shaft (36) that fits into the square hole (35) is formed in the male screw member (15B). The arm type valve gear according to claim 24, wherein the pivot member (15A) and the male screw member (15B) are integrally rotated by fitting the angular shaft (36) and the square hole (35). .
Applications Claiming Priority (10)
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JP2008-012484 | 2008-01-23 | ||
JP2008012484 | 2008-01-23 | ||
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JP2008016075A JP2009174487A (en) | 2008-01-28 | 2008-01-28 | Lash adjuster |
JP2008-016075 | 2008-01-28 | ||
JP2008-257395 | 2008-10-02 | ||
JP2008257395A JP2009197789A (en) | 2008-01-24 | 2008-10-02 | Lash adjuster |
JP2008-314617 | 2008-12-10 | ||
JP2008314617A JP2009197790A (en) | 2008-01-23 | 2008-12-10 | Arm type valve gear device |
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