WO2009081864A1 - ラッシュアジャスタ - Google Patents
ラッシュアジャスタ Download PDFInfo
- Publication number
- WO2009081864A1 WO2009081864A1 PCT/JP2008/073202 JP2008073202W WO2009081864A1 WO 2009081864 A1 WO2009081864 A1 WO 2009081864A1 JP 2008073202 W JP2008073202 W JP 2008073202W WO 2009081864 A1 WO2009081864 A1 WO 2009081864A1
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- WO
- WIPO (PCT)
- Prior art keywords
- screw
- side flank
- pressure side
- lash adjuster
- nut member
- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/143—Tappets; Push rods for use with overhead camshafts
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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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L1/0532—Camshafts overhead type the cams being directly in contact with the driven valve
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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 a lash adjuster incorporated in an engine valve gear.
- valve operating device that operates a valve provided in the intake port or exhaust port of an engine
- a valve lifter supported so as to be slidable up and down is pushed down by a cam, and the valve stem is pushed down by the valve lifter (direct valve operating device)
- One end of an arm supported so as to be swingable with the center as a fulcrum, and a valve stem pushed down at the other end of the arm rocker arm type valve gear
- a swing arm type valve operating device in which a central portion of an arm supported as a fulcrum is pushed down by a cam and a valve stem is pushed down at the other end of the arm.
- a lash adjuster is generally incorporated in the valve operating device, and the lash adjuster absorbs the change in the gap between the components of the valve operating device.
- a lash adjuster in the direct valve operating apparatus, a lifter body that is slidably inserted into a guide hole formed in the cylinder head, a nut member fixed to the lifter body, and a nut member
- An adjusting screw having a male screw on its outer periphery that engages with a female screw formed on the inner periphery, and a return spring that biases the adjusting screw in a direction protruding downward from the nut member, and the nut of the adjusting screw
- Patent Document 1 A device that presses a valve stem of a valve operating device with a protruding end from a member is known (Patent Document 1).
- the screw member is engaged with a nut member inserted into a receiving hole opened in the lower surface of the arm that swings according to the rotation of the cam, and a female screw formed on the inner periphery of the nut member.
- An adjusting screw having a male screw on the outer periphery thereof, and a return spring for biasing the adjusting screw in a direction protruding downward from the nut member, and a protruding end of the adjusting screw from the nut member What presses a valve stem is known (patent document 2).
- the swing arm type valve operating apparatus has a nut member inserted into a receiving hole opened in the upper surface of the cylinder head and a male screw engaged with a female screw formed on the inner periphery of the nut member on the outer periphery.
- the adjusting screw has a return spring that urges the adjusting screw in a direction protruding upward from the nut member, and the protruding end of the adjusting screw from the nut member supports the arm of the valve gear so as to swing.
- the adjusting screw moves in the axial direction while rotating in the nut member according to the change in position, and the valve operating device The change in the gap between the constituent members is absorbed.
- the lash adjuster smoothes the surface of the pressure side flank and causes friction between the pressure side flank. The coefficient becomes smaller. Therefore, when a load in the pushing direction is applied by the rotation of the cam, the adjustment screw moves in the pushing direction due to the slip between the pressure side flank, and the valve lift amount may be reduced.
- Patent Document 4 In order to suppress a decrease in the friction coefficient between the pressure side flank due to long-term use, a lash adjuster has been proposed in which one of the pressure side flank of the male screw and the pressure side flank of the female screw has a satin finish.
- each lash adjuster described above is required to reduce the axial length in order to increase the degree of freedom in engine design.
- the axial length of the lash adjuster is shortened, the meshing length between the male screw and the female screw is shortened, and as a result, the surface pressure acting between the pressure side flank of the male screw and the female screw is increased, resulting in wear of the male screw and the female screw. There was a problem that became easier to progress.
- the inventor of the present invention has studied a lash adjuster capable of suppressing the wear of the male screw and the female screw even when the engagement length of the male screw and the female screw is short, and the size of the backlash between the male screw and the female screw. Actual machine tests were conducted on a number of lash adjusters with different values.
- the problem to be solved by the present invention is to provide a lash adjuster in which the coefficient of friction between the pressure side flank of the male screw and the female screw is less likely to decrease when used for a long time, and to suppress wear of the male screw and the female screw of the lash adjuster. It is to be.
- a nut member having an internal thread on the inner periphery, an adjustment screw having an external thread that engages with the internal thread on the outer periphery, and a return that urges the adjustment screw in a direction protruding from the nut member
- a lash adjuster having a spring and receiving an axial load by the pressure side flank of the male screw and the female screw when an axial load in a direction of pushing the adjusting screw into the nut member is applied.
- the pressure side flank of the pressure side flank of the female screw is a satin finish, and the surface hardness of the satin finish is higher than the surface hardness of the other pressure side flank.
- the satin mentioned here is a surface composed of irregularities arranged irregularly.
- the return spring may be a compression coil spring that presses the adjusting screw in the axial direction, or a torsion spring that applies a rotational force in a direction protruding from the nut member to the adjusting screw.
- a compression coil spring is employed as the return spring
- the male screw and the female screw can be formed in a sawtooth shape in which the flank angle of the pressure side flank is larger than the flank angle of the play side flank.
- the surface roughness of the satin can be set in the range of Ra 1.6 to 12.5. Further, the satin finish may be formed by electric discharge machining or laser machining, but when formed by shot peening, the pressure side flank can be hardened to increase its durability.
- the surface hardness of the satin pressure side flank can be made higher than that of the other pressure side flank by, for example, coating of a hard film. Examples of the hard film include a titanium nitride film, a chromium nitride film, a diamond-like carbon film, and a ceramic. A membrane can be employed. Also, the surface hardness of the satin pressure side flank can be increased more than that of the other pressure side flank by carbonitriding or WPC treatment.
- the inventor of the present invention conducted an actual machine test on a large number of lash adjusters in which the backlash between the male screw and the female screw is different from each other. As a result, the backlash between the male screw and the female screw was set within a range of 0.1 to 0.4 mm. Then, compared with the case where a backlash was larger than 0.4 mm, it discovered that an external thread and an internal thread became very hard to wear.
- the nut member is fixed to a lifter body that is slidably inserted into a guide hole formed in a cylinder head, and the adjustment screw presses a valve stem of a valve operating device at a protruding end from the nut member.
- Direct adjust valve lash adjuster The nut member is inserted into a receiving hole opened on the lower surface of the arm that swings according to the rotation of the cam, and the adjustment screw is a rocker arm that presses the valve stem of the valve gear at the protruding end from the nut member.
- Type lash adjuster is a rocker arm that presses the valve stem of the valve gear at the protruding end from the nut member.
- a swing arm type valve operating device in which the nut member is inserted into a receiving hole opened in the upper surface of the cylinder head, and the adjusting screw supports the arm of the valve operating device in a swingable manner at a protruding end from the nut member. Rush adjuster.
- the lash adjuster of the present invention has a large uneven height of the pear texture compared to the wear amount.
- the surface of the side flank is difficult to be smooth, and the coefficient of friction between the pressure side flank is difficult to decrease.
- the surface hardness of the pressure side flank of the satin finish is higher than the surface hardness of the other pressure side flank, the wear of the satin finish is difficult to proceed, and the decrease in the friction coefficient between the pressure side flank can be effectively suppressed. .
- This lash adjuster has a matte pressure side flank of the male screw pressure side flank and female screw pressure side flank, so when the male screw and female screw pressure side flank approach each other, Oil film due to squeeze effect is difficult to form. Therefore, the axial load applied to the adjusting screw can be quickly received by the female screw of the nut member even at a low temperature when the viscosity of the lubricating oil is high.
- molybdenum disulfide is included even when oil added with organic molybdenum is used as a lubricating oil. It is difficult for the lubricating film to be formed on the surface of the hard film, and it is possible to more reliably prevent slippage between the pressure side flank of the male screw and the female screw.
- the backlash between the male screw and the female screw is set in the range of 0.1 to 0.4 mm
- the male screw and the female screw are extremely difficult to wear compared to the case where the backlash is larger than 0.4 mm. . Therefore, the engagement length between the male screw and the female screw can be set short, and the axial length of the lash adjuster can be shortened.
- Enlarged sectional view of the lash adjuster shown in FIG. Enlarged sectional view of the vicinity of the surface of the adjusting screw shown in FIG.
- FIG. 3 is an enlarged cross-sectional view showing a modification in which the female coating of the nut member is coated with the hard coating shown in FIG.
- the expanded sectional view which shows the backlash between the external thread of the lash adjuster shown in FIG. 1, and an internal thread The front view which shows the valve operating apparatus incorporating the lash adjuster of 2nd Embodiment of this invention.
- FIG. 6 is an enlarged sectional view of the lash adjuster shown in FIG. Front view showing a valve gear incorporating a lash adjuster according to a fifth embodiment of the present invention.
- FIG. 14 is an enlarged cross-sectional view of the lash adjuster shown in FIG. Front view showing a valve gear incorporating a lash adjuster according to a sixth embodiment of the present invention.
- FIG. 16 is an enlarged sectional view of the lash adjuster shown in FIG.
- FIG. 1 shows a valve gear incorporating a lash adjuster 1 according to the first embodiment of the present invention.
- This valve operating apparatus has a valve 4 provided in the intake port 3 of the cylinder head 2 and a valve stem 5 connected to the valve 4.
- the valve stem 5 extends upward from the valve 4, and an annular spring retainer 6 is fixed to the upper outer periphery of the valve stem 5.
- the spring retainer 6 is urged upward by a valve spring 7, and the valve 4 is seated on the valve seat 8 by the urging force.
- the lash adjuster 1 includes a lifter body 9, a nut member 10, an adjustment screw 11, and a return spring 12.
- the lifter body 9 is slidably inserted in a guide hole 13 formed in the cylinder head 2.
- the lifter body 9 includes a cylindrical portion 9a and an end plate 9b that closes the upper end of the cylindrical portion 9a.
- a cam 15 fixed to the cam shaft 14 is provided above the lifter body 9. When the cam shaft 14 rotates, the cam peak portion 15b raised from the base circle 15a presses the upper surface of the end plate 9b and pushes the lifter body 9 down.
- the nut member 10 is fixed to the lower surface of the end plate 9 b with a retaining ring 16, and a female screw 17 formed on the inner periphery of the nut member 10 is formed on the outer periphery of the adjustment screw 11.
- the male screw 18 is engaged with the screw.
- the male screw 18 is formed in a sawtooth shape in which the flank angle of the pressure side flank 19 that receives pressure when an axial load in the direction of pushing the adjusting screw 11 into the nut member 10 is applied is larger than the flank angle of the play side flank 20. ing.
- the female screw 17 is also formed in a sawtooth shape in which the flank angle of the pressure-side flank 21 that receives pressure when a load in the direction of pushing the adjusting screw 11 into the nut member 10 is applied is larger than the flank angle of the play-side flank 22. .
- the protruding end of the adjusting screw 11 from the nut member 10 is in contact with the spacer 23.
- the spacer 23 is prevented from rotating with respect to the nut member 10 by a retainer 24 fixed by a retaining ring 16, and can move up and down within a range of a notch 25 formed in the retainer 24.
- the end plate 9b of the lifter body 9 is formed with an oil passage hole 26 penetrating vertically, and the lubricating oil supplied to the upper surface of the end plate 9b is introduced into the nut member 10 through the oil passage hole 26. It has become so.
- the lubricating oil introduced into the nut member 10 lubricates the male screw 18 and the female screw 17.
- the male screw 18 of the adjusting screw 11 is shot peened and coated with a hard film 27, whereby the pressure-side flank 19 of the male screw 18 is a satin finish, and its surface hardness Is higher than the surface hardness of the pressure side flank 19 of the female screw 17.
- the surface roughness of the satin finish is set in the range of Ra 1.6 to 12.5, the uneven height of the satin finish can be surely increased as compared with the wear amount.
- the hard coating 27 include a titanium nitride (TiN) film, a chromium nitride (CrN) film, a diamond-like carbon (DLC) film, and a ceramic film.
- the pressure side flank 21 of the female screw 17 is formed to have a smaller surface roughness than the pressure side flank 19 of the male screw 18. Further, as shown in FIG. 5, a backlash b (a gap in the axial direction) is provided between the male screw 18 and the female screw 17, and the backlash b is set in a range of 0.1 to 0.4 mm. .
- the return spring 12 is a compression coil spring, and is assembled between the adjustment screw 11 and the end plate 9b of the lifter body 9 while being compressed in the axial direction.
- the return spring 12 is supported at its upper end by the end plate 9b, and its lower end presses the adjusting screw 11 in the axial direction.
- the adjusting screw 11 is urged in a direction protruding downward from the nut member 10. ing.
- the protruding end of the adjustment screw 11 from the nut member 10 presses the upper end of the valve stem 5 via a spacer 23 as shown in FIG.
- the cam of the cam 15 When a difference in thermal expansion occurs between the components of the valve operating device such as the cylinder head 2 and the valve stem 5 during engine operation, and the distance between the cam 15 and the lifter body 9 increases, the cam of the cam 15 The amount of protrusion of the adjusting screw 11 when the cam 15 rotates and the load in the pushing direction is released is larger than the amount of pushing of the adjusting screw 11 when the peak portion 15b pushes down the lifter body 9. As a result, each time the cam 15 rotates, the adjusting screw 11 gradually moves in the protruding direction, so that no gap is generated between the base circle 15 a of the cam 15 and the end plate 9 b of the lifter body 9.
- the lash adjuster 1 When the pressure side flank 19 of the male screw 18 is worn due to long-term use, the lash adjuster 1 has a high textured unevenness compared to the amount of wear, so that the pressure side flank 19 of the male screw 18 The surface is less likely to be smooth, and the friction coefficient between the pressure side flanks 19 and 21 of the male screw 18 and the female screw 17 is difficult to decrease. Therefore, it is possible to prevent excessive slippage between the pressure side flanks 19 and 21 of the male screw 18 and the female screw 17 when a load in the pushing direction is applied to the adjusting screw 11 by the rotation of the cam 15.
- the lash adjuster 1 employs a titanium nitride film, a chromium nitride film, a diamond-like carbon film, or a ceramic film as the hard film 27, an oil to which molybdenum dithiocarbamate (MoDTC) or molybdenum dithiophosphate (MoDTP) is added.
- MoDTC molybdenum dithiocarbamate
- MoDTP molybdenum dithiophosphate
- FM oil molybdenum dithiocarbamate
- MoS 2 molybdenum disulfide
- the backlash b between the male screw 18 and the female screw 17 is 0.4 mm or less, the male screw 18 and the female screw 17 have a larger backlash b than 0.4 mm. Extremely difficult to wear. Therefore, the engagement length between the male screw 18 and the female screw 17 can be set short, and the axial length of the lash adjuster 1 can be suppressed.
- the backlash b between the male screw 18 and the female screw 17 is 0.1 mm or more in the lash adjuster 1, the load in the pushing direction is released as compared with the case where the backlash b is smaller than 0.1 mm.
- the adjustment screw 11 is turned, the rotation of the adjustment screw 11 is smooth, and stable performance can be exhibited.
- the surface hardness of the pressure side flank 19 of the male screw 18 is higher than the surface hardness of the pressure side flank 21 of the female screw 17 by coating the male screw 18 with the hard coating 27.
- the surface hardness of the pressure side flank 19 of the male screw 18 may be increased by performing nitriding treatment.
- the pressure side flank 19 of the male screw 18 may be made into a satin surface by performing a WPC process on the male screw 18 of the adjusting screw 11.
- the WPC process is a shot peening that raises the surface temperature of the male screw 18 to the A3 transformation point or higher, for example, a process of injecting a shot of 40 to 200 ⁇ m toward the surface of the male screw 18 at a speed of 100 m / min or more. It is.
- the retained austenite on the surface of the male screw 18 is martensitic, and the surface structure of the male screw 18 is recrystallized and refined, so that the surface hardness of the male screw 18 is higher than the pressure side flank 21 of the female screw 17. be able to.
- the male screw 18 can be coated with a hard coating 27 after shot peening is applied to the entire surface thereof.
- the play side flank 20 of the male screw 18 also becomes a matte surface, and the surface hardness of the matte surface is higher than the surface hardness of the play side flank 22 of the female screw 17, so that the play side flank of the male screw 18 is used over a long period of use. Even when 20 is worn, the coefficient of friction between the play side flank 20, 22 of the male screw 18 and the female screw 17 can be maintained.
- the said satin can be formed also by electrical discharge machining or laser processing, if it forms by shot peening as shown in the said embodiment, the pressure side flank 19 can be hardened and the durability can be improved.
- the pressure side flank 19 of the male screw 18 and the pressure side flank 21 of the female screw 17 is a matte surface, and the surface hardness of the matte surface is the surface hardness of the pressure side flank 21 of the female screw 17.
- the pressure side flank 21 of the female screw 17 is made into a matte surface, and the surface hardness of the pressure side flank 19 of the male screw 18 is made surface. May be higher.
- the female screw 17 can be coated with the hard coating 27 after shot peening is applied to the entire surface thereof. As a result, even when the play-side flank 22 of the female screw 17 is worn due to long-term use, the friction coefficient between the play-side flank 20, 22 of the male screw 18 and the female screw 17 can be maintained.
- FIG. 6 shows a valve gear incorporating the lash adjuster 31 according to the second embodiment of the present invention.
- portions corresponding to those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
- This valve operating apparatus has an arm 33 that is supported at the center by a fulcrum shaft 32 so as to be swingable.
- a roller 34 is attached to one end of the arm 33, and a lash adjuster 31 is incorporated in the other end.
- a cam 15 fixed to the camshaft 14 is in contact with the roller 34, and the arm 33 swings when the camshaft 14 rotates.
- the lash adjuster 31 includes a nut member 35, an adjustment screw 36, and a return spring 37.
- the nut member 35 is inserted into a receiving hole 38 penetrating the arm 33 vertically, and the female screw 17 formed on the inner periphery of the nut member 35 engages with the male screw 18 formed on the outer periphery of the adjusting screw 36. is doing.
- the pressure side flank 19 of the male screw 18 is a matte surface by shot peening as in the first embodiment, and the surface hardness of the matte surface is obtained by coating the male screw 18 with the hard film 27 to thereby form the pressure side flank of the female screw 17. It is higher than the surface hardness of 21.
- a backlash b is provided between the male screw 18 and the female screw 17 (see FIG. 7), and the backlash b is set in a range of 0.1 to 0.4 mm.
- the upper end of the nut member 35 protrudes from the upper surface of the arm 33, and a bottomed cylindrical cap 39 is fitted and fixed to the protruding portion with a tightening margin.
- the cap 39 is locked to the upper edge of the accommodation hole 38 to prevent the nut member 35 from dropping from the accommodation hole 38 downward.
- the cap 39 is formed with an oil passage hole 40 penetrating vertically, so that the lubricating oil supplied to the upper surface of the arm 33 is introduced into the nut member 35 through the oil passage hole 40. It has become.
- a flange 41 that contacts the lower surface of the arm 33 is formed at the lower end of the nut member 35, and the upward force acting on the nut member 35 is received by the flange 41.
- the return spring 37 is a compression coil spring, and is assembled between the cap 39 and the adjustment screw 36 in a state of being compressed in the axial direction.
- the return spring 37 has an upper end supported by a cap 39 and a lower end pressing the adjusting screw 36 in the axial direction. By the pressing, the adjusting spring 36 is urged in a direction protruding downward from the nut member 35. Yes. The protruding end of the adjustment screw 36 from the nut member 35 presses the upper end of the valve stem 5.
- the lash adjuster 31 has a high textured unevenness when the pressure side flank 19 of the male screw 18 is worn. Since the surface is difficult to be smooth, the friction coefficient between the pressure side flank 19, 21 of the male screw 18 and the female screw 17 is unlikely to decrease. Further, since the surface hardness of the pressure side flank 19 of the male screw 18 which is a matte surface is higher than the surface hardness of the pressure side flank 21 of the female screw 17, the wear of the matte surface is difficult to proceed, and the friction coefficient between the pressure side flank 19, 21 Can be effectively suppressed.
- the pressure side flank 19 of the male screw 18 is a matte surface in the lash adjuster 31, when the pressure side flank 19, 21 of the male screw 18 and the female screw 17 approach each other, the pressure side flank 19, 21 In addition, it is difficult to form an oil film due to the squeeze effect.
- the backlash b between the male screw 18 and the female screw 17 is 0.4 mm or less in the lash adjuster 31
- the male screw 18 and the female screw 17 have a larger backlash b than 0.4 mm. Extremely difficult to wear. Therefore, the engagement length between the male screw 18 and the female screw 17 can be set short, and the axial length of the lash adjuster 31 can be suppressed.
- the backlash b between the male screw 18 and the female screw 17 is 0.1 mm or more in the lash adjuster 31, the load in the pushing direction is released compared with the case where the backlash b is smaller than 0.1 mm.
- the adjustment screw 36 is rotated, the rotation of the adjustment screw 36 is smooth, and stable performance can be exhibited.
- FIG. 8 shows a valve gear incorporating a lash adjuster 51 according to a third embodiment of the present invention.
- portions corresponding to those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
- This valve operating apparatus has an arm 52 that is supported at one end by a lash adjuster 51 so as to be swingable and whose other end contacts the upper end of the valve stem 5.
- a cam 15 fixed to the camshaft 14 is provided above the arm 52. When the camshaft 14 rotates, the arm 52 swings with the lash adjuster 51 as a fulcrum.
- the lash adjuster 51 includes a nut member 53, an adjustment screw 54, and a return spring 55.
- the nut member 53 is inserted into the accommodation hole 56 opened on the upper surface of the cylinder head 2, and the female screw 17 formed on the inner periphery of the nut member 53 is screwed with the male screw 18 formed on the outer periphery of the adjustment screw 54. Match.
- the pressure side flank 19 of the male screw 18 is a matte surface by shot peening as in the first embodiment, and the surface hardness of the matte surface is obtained by coating the male screw 18 with the hard film 27 to thereby form the pressure side flank of the female screw 17. It is higher than the surface hardness of 21. Further, the backlash between the male screw 18 and the female screw 17 is set in a range of 0.1 to 0.4 mm.
- a bottom member 57 is fixed to the lower end of the nut member 53.
- the return spring 55 is a compression coil spring and is incorporated between the adjustment screw 54 and the bottom member 57 in a state of being compressed in the axial direction.
- the return spring 55 has a lower end supported by a bottom member 57 and an upper end pressing the adjusting screw 54 in the axial direction via a spring seat 58, and the adjusting screw 54 protrudes upward from the nut member 53 by the pressing. It is energizing in the direction to do.
- the protruding end of the adjustment screw 54 from the nut member 53 is fitted into a recess 59 formed on the lower surface of the arm 52 to support the arm 52 so as to be swingable.
- the lash adjuster 51 has a textured unevenness that is larger than the wear amount when the pressure side flank 19 of the male screw 18 is worn. Since the surface is difficult to be smooth, the friction coefficient between the pressure side flank 19, 21 of the male screw 18 and the female screw 17 is unlikely to decrease. Further, since the surface hardness of the pressure side flank 19 of the male screw 18 which is a matte surface is higher than the surface hardness of the pressure side flank 21 of the female screw 17, the wear of the matte surface is difficult to proceed, and the friction coefficient between the pressure side flank 19, 21 Can be effectively suppressed.
- the lash adjuster 51 since the pressure side flank 19 of the male screw 18 is a matte surface, the lash adjuster 51 has the pressure side flank 19 and 21 close to the pressure side flank 19 and 21 when the male screw 18 and the female screw 17 come close to each other. Oil film due to squeeze effect is difficult to form.
- the backlash between the male screw 18 and the female screw 17 is 0.4 mm or less in the lash adjuster 51, the male screw 18 and the female screw 17 are extremely worn compared to the case where the backlash is larger than 0.4 mm. Hard to do. Therefore, the engagement length between the male screw 18 and the female screw 17 can be set short, and the axial length of the lash adjuster 51 can be suppressed.
- the backlash between the male screw 18 and the female screw 17 is 0.1 mm or more in the lash adjuster 51, the load in the pushing direction is released as compared with the case where the backlash is smaller than 0.1 mm.
- the adjustment screw 54 rotates smoothly, stable performance can be exhibited.
- the following items 1) to 3) are performed.
- a large number of samples having different backlash sizes between the male screw 18 and the female screw 17 are prepared, and each sample is assembled in an actual engine to perform a durability test. The relationship between backlash after endurance was investigated.
- the lash adjuster 51 having a meshing length of the male screw 18 and the female screw 17 is 1 ⁇ 2 that of the prior art.
- the increase in the backlash due to the durability test is small for the sample having the same screw engagement length as the conventional one regardless of the size of the initial backlash.
- the initial backlash is larger than 0.4 mm.
- the initial backlash is set to a size of 0.4 mm or less so that the male screw It can be seen that the wear of the 18 and the internal thread 17 can be very effectively suppressed.
- the maximum surface pressure acting between the pressure-side flanks 19 and 21 of the male screw 18 and the female screw 17 was measured. 10 MPa, the screw engagement length of the conventional sample of 1/2 was 20 MPa, and the screw engagement length of the conventional 1/3 sample was 30 MPa.
- FIGS. 12 and 13 show a valve gear incorporating a lash adjuster 71 according to a fourth embodiment of the present invention.
- portions corresponding to those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
- the adjustment screw 11 has a male screw 73 on its outer periphery that engages with a female screw 72 formed on the inner periphery of the nut member 10.
- the male screw 73 and the female screw 72 are vertically trapezoidal trapezoidal screws, and when an axial load is applied in the direction in which the adjusting screw 11 is pushed into the nut member 10, the axial load is applied to the pressure of the male screw 73 and the female screw 72.
- the side flanks 74 and 75 are designed to receive it.
- the pressure side flank 74 of the male screw 73 is made into a matte surface having a surface roughness of Ra 1.6 to 12.5 by shot peening, as in the first embodiment. As a result, the surface hardness of the pressure side flank 75 of the internal thread 72 is increased.
- a backlash is provided between the male screw 73 and the female screw 72, and the backlash is set in a range of 0.1 to 0.4 mm.
- a torsion coil spring 76 is incorporated between the adjusting screw 11 and the end plate 9b of the lifter body 9.
- the upper end of the torsion coil spring 76 is inserted into a locking groove 77 formed on the upper surface of the nut member 10 and is prevented from rotating, and the lower end is locked in a locking hole 78 formed in the adjusting screw 11.
- Rotational force in a direction protruding downward from the nut member 10 is applied to the adjusting screw 11 by the torsional deformation.
- the protruding end of the adjusting screw 11 from the nut member 10 presses the upper end of the valve stem 5 via the spacer 23.
- the lash adjuster 71 has a large uneven surface height even when the pressure side flank of the male screw 73 is worn, and the surface of the pressure side flank of the male screw 73 is not easily smoothed. 73 and the friction coefficient between the pressure side flanks 74 and 75 of the female screw 72 are unlikely to decrease. Further, since the surface hardness of the pressure side flank 74 of the male screw 73 which is a matte surface is higher than the surface hardness of the pressure side flank 75 of the female screw 72, the wear of the matte surface is difficult to proceed, and the friction coefficient between the pressure side flanks 74 and 75 Can be effectively suppressed.
- the pressure side flank of the male screw 73 is a matte surface in the lash adjuster 71, when the pressure side flank 74, 75 of the male screw 73 and the female screw 72 come close to each other, the pressure side flank 74, 75 is interposed between the pressure side flank 74, 75. Oil film due to squeeze effect is difficult to form.
- the torsion coil spring 76 is employed as the torsion spring that applies the rotational force in the direction protruding from the nut member 10 to the adjustment screw 11.
- a mainspring spring is employed instead of the torsion coil spring 76. Also good.
- FIG. 14 and 15 show a valve operating apparatus incorporating a lash adjuster 91 according to a fifth embodiment of the present invention.
- portions corresponding to those of the second embodiment are denoted by the same reference numerals, and description thereof is omitted.
- the nut member 35 is inserted into a receiving hole 92 opened on the lower surface of the arm 33, and a female screw 93 formed on the inner periphery thereof is screw-engaged with a male screw 94 formed on the outer periphery of the adjusting screw 36.
- the male screw 94 and the female screw 93 are vertically symmetrical triangular screws, and when an axial load is applied in the direction in which the adjusting screw 36 is pushed into the nut member 35, the axial load is applied to the pressure side flank 95 of the male screw 94 and the female screw 93. , 96.
- the pressure side flank 95 of the male screw 94 is made into a matte surface having a surface roughness of Ra 1.6 to 12.5 by shot peening, as in the second embodiment. By coating the surface, the surface hardness of the pressure side flank of the female screw 93 is increased.
- a backlash is provided between the male screw 94 and the female screw 93, and the backlash is set in a range of 0.1 to 0.4 mm.
- a torsion coil spring 97 is incorporated between the adjusting screw 36 and the inner bottom surface of the accommodation hole 92.
- the upper end of the torsion coil spring 97 is inserted into a through hole 98 formed in the inner bottom surface of the accommodation hole 92 and is prevented from rotating, and the lower end is engaged with an engagement hole 99 formed in the adjustment screw 36. Due to the torsional deformation, a rotational force in a direction protruding downward from the nut member 35 is applied to the adjusting screw 36. The protruding end of the adjustment screw 36 from the nut member 35 presses the upper end of the valve stem 5.
- the engine oil splashed on the upper surface of the arm 33 is introduced into the accommodation hole 92 through the through hole 98 and lubricates between the male screw 94 and the female screw 93.
- the lash adjuster 91 When the pressure side flank 95 of the male screw 94 is worn, the lash adjuster 91 has a high textured surface unevenness compared to the amount of wear, and the surface of the pressure side flank 95 of the male screw 94 is difficult to smooth. The friction coefficient between the pressure side flanks 95 and 96 of the male screw 94 and the female screw 93 is unlikely to decrease. Further, since the surface hardness of the pressure side flank 95 of the male screw 94 made of a matte surface is higher than the surface hardness of the pressure side flank 96 of the female screw 93, the wear of the matte surface is difficult to proceed, and the friction coefficient between the pressure side flank 95 and 96 Can be effectively suppressed.
- the pressure side flank 95 of the male screw 94 is matte, so when the pressure side flank 95, 96 of the male screw 94 and the female screw 93 approach each other, the pressure side flank 95, 96 is between In addition, it is difficult to form an oil film due to the squeeze effect.
- a torsion coil spring 97 is employed as a torsion spring that applies a rotational force in a direction protruding from the nut member 35 to the adjustment screw 36.
- a mainspring spring is employed instead of the torsion coil spring 97. Also good.
- FIG. 16 and 17 show a valve gear incorporating the lash adjuster 111 according to the sixth embodiment of the present invention.
- parts corresponding to those of the third embodiment are denoted by the same reference numerals, and description thereof is omitted.
- the nut member 53 has a female screw 17 on the lower inner periphery.
- the adjusting screw 54 includes a male screw member 54A having a male screw 18 on the outer periphery thereof that engages with the female screw 17 of the nut member 53, and a pivot member 54B fitted into the nut member 53 so as to be slidable in the axial direction.
- a disc spring 112 is incorporated between the pivot member 54B and the male screw member 54A, and the insertion end of the pivot member 54B into the nut member 53 is supported by the male screw member 54A via the disc spring 112.
- the disc spring 112 is compressed when the engine is cooled and a contraction difference is generated between the constituent members of the valve operating apparatus, and absorbs the contraction difference between the constituent members. Therefore, when the engine is restarted, a gap due to a contraction difference between the constituent members of the valve operating device does not occur between the valve 4 and the valve seat 8, and compression leakage does not occur.
- the male screw 18 is shot peened and coated with a hard film.
- the pressure side flank 19 of the male screw 18 is a satin finish, and the surface roughness of the satin finish is Ra 1.6. It is in the range of ⁇ 12.5.
- the surface hardness of the matte surface is higher than the surface hardness of the pressure side flank 21 of the female screw 17 by coating the male screw 18 with a hard film.
- a torsion coil spring 114 is incorporated between the male screw member 54A and the bottom 113 of the nut member 53, as shown in FIG.
- the lower end of the torsion coil spring 114 is inserted into a through hole 115 formed in the bottom 113 of the nut member 53 and is prevented from rotating, and the upper end is engaged with an engagement hole 116 formed in the male screw member 54A.
- the pivot member 54 ⁇ / b> B has a hemispherical protruding end 117 from the nut member 53, and the protruding end 117 fits into a recess 59 formed on the lower surface of the end of the arm 52.
- the arm 52 is swingably supported.
- An oil drain hole 118 communicating with the through hole 115 is formed on the inner bottom surface of the accommodation hole 56. Therefore, the engine oil that has flowed into the nut member 53 from the upper end surface of the nut member 53 through the gap between the male screw 18 and the female screw 17 passes through the through hole 115 and the oil drain hole 118 in order, and is discharged from the nut member 53. .
- the lash adjuster 111 When the pressure side flank of the male screw 18 is worn, the lash adjuster 111 has a large uneven surface height compared to the amount of wear, and the surface of the pressure side flank 19 of the male screw 18 is not easily smoothed.
- the friction coefficient between the pressure-side flanks 19 and 21 of the male screw 18 and the female screw 17 is difficult to decrease. Further, since the surface hardness of the pressure side flank 19 of the male screw 18 which is a matte surface is higher than the surface hardness of the pressure side flank 21 of the female screw 17, the wear of the matte surface is difficult to proceed, and the friction coefficient between the pressure side flank 19, 21 Can be effectively suppressed.
- the pressure side flank 19 of the male screw 18 and the pressure side flank 21 of the female screw 17 is a matte surface, but shot peening is applied to the female screw 17 as shown in FIG. 4.
- the pressure side flank 21 of the female screw 17 may be a satin finish, and the surface hardness thereof may be higher than the surface hardness of the pressure side flank 19 of the male screw 18.
- the internal thread 17 may perform shot peening only on the pressure side flank 21 of the surface, or may perform shot peening on the entire surface.
- a torsion coil spring is used as a torsion spring that applies a rotational force in a direction protruding from the nut member 53 to the adjustment screw 54.
- a mainspring spring may be used instead of the torsion coil spring. .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
1)前記ナット部材は、シリンダヘッドに形成されたガイド孔に上下にスライド可能に挿入されるリフタボディに固定され、前記アジャストスクリュは、ナット部材からの突出端で動弁装置のバルブステムを押圧するダイレクト式動弁装置のラッシュアジャスタ。
2)前記ナット部材は、カムの回転に応じて揺動するアームの下面に開口した収容穴に挿入され、前記アジャストスクリュは、ナット部材からの突出端で動弁装置のバルブステムを押圧するロッカアーム式動弁装置のラッシュアジャスタ。
3)前記ナット部材は、シリンダヘッドの上面に開口した収容穴に挿入され、前記アジャストスクリュは、ナット部材からの突出端で動弁装置のアームを揺動可能に支持するスイングアーム式動弁装置のラッシュアジャスタ。
2 シリンダヘッド
5 バルブステム
9 リフタボディ
10 ナット部材
11 アジャストスクリュ
12 リターンスプリング
13 ガイド孔
15 カム
17 雌ねじ
18 雄ねじ
19 圧力側フランク
20 遊び側フランク
21 圧力側フランク
22 遊び側フランク
27 硬質皮膜
31 ラッシュアジャスタ
33 アーム
35 ナット部材
36 アジャストスクリュ
37 リターンスプリング
38 収容穴
51 ラッシュアジャスタ
52 アーム
53 ナット部材
54 アジャストスクリュ
55 リターンスプリング
56 収容穴
76 ねじりコイルばね
b バックラッシ
1)雄ねじ18と雌ねじ17の噛み合い長さが従来と同等のラッシュアジャスタ51
2)雄ねじ18と雌ねじ17の噛み合い長さが従来の1/2のラッシュアジャスタ51
3)雄ねじ18と雌ねじ17の噛み合い長さが従来の1/3のラッシュアジャスタ51
エンジン回転数:6000rpm
エンジン排気量:1500cc
エンジンオイル:0W-20(SAE粘度)
耐久時間 :500時間
トピーニングを雌ねじ17に施すことで、雌ねじ17の圧力側フランク21を梨地とし、かつ、その表面硬度を雄ねじ18の圧力側フランク19の表面硬度よりも高くしてもよい。この場合も、雌ねじ17は、その表面のうちの圧力側フランク21のみにショットピーニングを施してもよく、その表面全体にショットピーニングを施してもよい。
Claims (13)
- 内周に雌ねじ(17)を有するナット部材(10)と、前記雌ねじ(17)にねじ係合する雄ねじ(18)を外周に有するアジャストスクリュ(11)と、そのアジャストスクリュ(11)を前記ナット部材(10)から突出する方向に付勢するリターンスプリング(12)とを有し、前記アジャストスクリュ(11)をナット部材(10)に押し込む方向の軸方向荷重を負荷したときに、その軸方向荷重を前記雄ねじ(18)と雌ねじ(17)の圧力側フランク(19,21)で受けるラッシュアジャスタ(1)において、前記雄ねじ(18)の圧力側フランク(19)と前記雌ねじ(17)の圧力側フランク(21)のうちの一方を梨地とし、その梨地の表面硬度を他方の圧力側フランク(19,21)の表面硬度よりも高くしたことを特徴とするラッシュアジャスタ。
- 前記リターンスプリング(12)は、前記アジャストスクリュ(11)を軸方向に押圧する圧縮コイルばねであり、前記雄ねじ(18)と雌ねじ(17)は、前記圧力側フランク(19,21)のフランク角が遊び側フランク(20,22)のフランク角よりも大きい鋸歯状である請求項1に記載のラッシュアジャスタ。
- 前記リターンスプリングは、前記アジャストスクリュ(11)にナット部材(10)から突出する方向の回転力を付与するねじりばね(76)である請求項1に記載のラッシュアジャスタ。
- 前記梨地の表面粗さをRa1.6~12.5の範囲に設定した請求項1から3のいずれかに記載のラッシュアジャスタ。
- 前記梨地をショットピーニングにより形成した請求項1から4のいずれかに記載のラッシュアジャスタ。
- 硬質皮膜(27)のコーティングによって、梨地の圧力側フランク(19)の表面硬度を他方の圧力側フランク(21)よりも高めた請求項1から5のいずれかに記載のラッシュアジャスタ。
- 前記硬質皮膜(27)が、窒化チタン膜、窒化クロム膜、ダイヤモンドライクカーボン膜、セラミック膜のいずれかである請求項6に記載のラッシュアジャスタ。
- 浸炭窒化処理によって、梨地の圧力側フランク(19)の表面硬度を他方の圧力側フランク(21)よりも高めた請求項1から5のいずれかに記載のラッシュアジャスタ。
- WPC処理によって、梨地の圧力側フランク(19)の表面硬度を他方の圧力側フランク(21)よりも高めた請求項1から5のいずれかに記載のラッシュアジャスタ。
- 前記雄ねじ(18)と前記雌ねじ(17)の間のバックラッシ(b)を0.1~0.4mmの範囲に設定した請求項1から9のいずれかに記載のラッシュアジャスタ。
- 前記ナット部材(10)は、シリンダヘッド(2)に形成されたガイド孔(13)に上下にスライド可能に挿入されるリフタボディ(9)に固定され、前記アジャストスクリュ(11)は、ナット部材(10)からの突出端で動弁装置のバルブステム(5)を押圧する請求項1から10のいずれかに記載のラッシュアジャスタ。
- 前記ナット部材(35)は、カム(15)の回転に応じて揺動するアーム(33)の下面に開口した収容穴(38)に挿入され、前記アジャストスクリュ(36)は、ナット部材(35)からの突出端で動弁装置のバルブステム(5)を押圧する請求項1から10のいずれかに記載のラッシュアジャスタ。
- 前記ナット部材(53)は、シリンダヘッド(2)の上面に開口した収容穴(56)に挿入され、前記アジャストスクリュ(54)は、ナット部材(53)からの突出端で動弁装置のアーム(52)を揺動可能に支持する請求項1から10のいずれかに記載のラッシュアジャスタ。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/746,546 US20100263614A1 (en) | 2007-12-25 | 2008-12-19 | Lash adjuster |
DE112008003546T DE112008003546T5 (de) | 2007-12-25 | 2008-12-19 | Ventilspiel-Einstellvorrichtung |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007331759 | 2007-12-25 | ||
JP2007-331759 | 2007-12-25 | ||
JP2008-077648 | 2008-03-25 | ||
JP2008077648 | 2008-03-25 | ||
JP2008257483A JP2009257306A (ja) | 2007-12-25 | 2008-10-02 | ラッシュアジャスタ |
JP2008-257483 | 2008-10-02 |
Publications (1)
Publication Number | Publication Date |
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WO2009081864A1 true WO2009081864A1 (ja) | 2009-07-02 |
Family
ID=40801165
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2008/073202 WO2009081864A1 (ja) | 2007-12-25 | 2008-12-19 | ラッシュアジャスタ |
Country Status (4)
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US (1) | US20100263614A1 (ja) |
JP (1) | JP2009257306A (ja) |
DE (1) | DE112008003546T5 (ja) |
WO (1) | WO2009081864A1 (ja) |
Families Citing this family (2)
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DE112008003314T5 (de) * | 2007-12-07 | 2010-10-21 | NTN Corporation, Osaka-shi | Spielausgleichsvorrichtung |
JP2011127533A (ja) * | 2009-12-18 | 2011-06-30 | Ntn Corp | アーム式動弁装置 |
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JP2003227318A (ja) | 2002-02-06 | 2003-08-15 | Ntn Corp | 動弁装置におけるラッシュアジャスタ |
JP2004346821A (ja) * | 2003-05-22 | 2004-12-09 | Ntn Corp | アーム式動弁装置 |
JP4103849B2 (ja) | 2003-05-28 | 2008-06-18 | ヤマハ株式会社 | D/aコンバータ |
JP4603304B2 (ja) * | 2004-07-20 | 2010-12-22 | Ntn株式会社 | 密封型転がり軸受 |
JP2006132426A (ja) | 2004-11-05 | 2006-05-25 | Ntn Corp | アーム式動弁装置 |
DE602006021498D1 (de) * | 2005-03-11 | 2011-06-09 | Ntn Toyo Bearing Co Ltd | Wälzlager |
DE112009000693T5 (de) * | 2008-03-24 | 2011-03-24 | NTN Corporation, Osaka-shi | Spielausgleichsvorrichtung |
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2008
- 2008-10-02 JP JP2008257483A patent/JP2009257306A/ja active Pending
- 2008-12-19 WO PCT/JP2008/073202 patent/WO2009081864A1/ja active Application Filing
- 2008-12-19 DE DE112008003546T patent/DE112008003546T5/de not_active Withdrawn
- 2008-12-19 US US12/746,546 patent/US20100263614A1/en not_active Abandoned
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JPH06193412A (ja) * | 1992-09-23 | 1994-07-12 | Eaton Corp | 直動油圧式タペットの製造方法および該方法により製造された油圧直動式タペット |
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JP2007092668A (ja) * | 2005-09-29 | 2007-04-12 | Ntn Corp | アーム式動弁装置 |
Also Published As
Publication number | Publication date |
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DE112008003546T5 (de) | 2010-10-28 |
JP2009257306A (ja) | 2009-11-05 |
US20100263614A1 (en) | 2010-10-21 |
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