US20120318216A1 - Tappet roller bearing - Google Patents

Tappet roller bearing Download PDF

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Publication number
US20120318216A1
US20120318216A1 US13/060,206 US201113060206A US2012318216A1 US 20120318216 A1 US20120318216 A1 US 20120318216A1 US 201113060206 A US201113060206 A US 201113060206A US 2012318216 A1 US2012318216 A1 US 2012318216A1
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Prior art keywords
roller
roller bearing
rollers
tappet
axial direction
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Abandoned
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US13/060,206
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English (en)
Inventor
Tomohiro Kudo
Satoshi Hachisuka
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NSK Ltd
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NSK Ltd
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Assigned to NSK LTD. reassignment NSK LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HACHISUKA, SATOSHI, KUDO, TOMOHIRO
Publication of US20120318216A1 publication Critical patent/US20120318216A1/en
Abandoned legal-status Critical Current

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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
    • F01L1/18—Rocking arms or levers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • F01L2305/02—Mounting of rollers

Definitions

  • the present invention relates to a tappet roller bearing and, specifically, the invention relates to a tappet roller bearing to be mounted into a cam follow apparatus which is used in the variable valve mechanism of an engine.
  • variable valve mechanism which changes the opening and closing timing of one or both of a suction valve or an exhaust valve according to the changes of the rotation speed of the engine.
  • Such variable valve mechanism is generally constituted of a cam follower apparatus including a locker arm for a high speed cam and a locker arm for a low speed cam.
  • cam follower apparatus which includes a lock arm for high speed and low speed cams and also which, in operation, slides these cams in the axial direction thereof to thereby switch the high speed and low speed cams over to each other.
  • the cam follower apparatus includes a locker arm which is disposed opposed to a cam fixed to a cam shaft rotatable in synchronization with the crankshaft of the engine and has a roller to receive the movement of the cam (see, for example, the patent reference 1 to 3).
  • a cam follower apparatus disclosed in the patent reference 1 in the intermediate portion of a locker arm, there is provided a support shaft and, on this support shaft, there are rotatably supported multiple tappet rollers which can be contacted with the cam fixed to the cam shaft.
  • a cam follower apparatus which is disclosed in the patent reference 2 and is mounted on the end portion of a locker arm, there are included: a shaft the two end portions of which are respectively supported on a pair of support plates and also which is used to constitute an inner race; three outer races respectively interposed between the pair of support plates; and, multiple rollers respectively interposed between the shaft and three outer races and each having a length extending over the whole of the three outer races.
  • a shaft the two end portions of which are respectively supported on a pair of support plates and also which is used to constitute an inner race; two outer races respectively interposed between the pair of support plates; and, multiple rollers respectively interposed between the shaft and two outer races and each having a length extending over the whole of the two outer races.
  • a shaft the two end portions of which are respectively supported on a pair of support plates and also which is used to constitute an inner race; an outer race interposed between the pair of support plates through a washer; and, multiple rollers respectively interposed between the shaft and outer race and arranged in two lines in the axial direction of the roller bearing through a spacer.
  • Patent Reference 1 U.S. Pat. No. 6,532,920 Specification
  • Patent Reference 2 German Patent Application No. 102006018512 Specification
  • Patent Reference 3 Japanese Patent Publication No. 2009-293392
  • Patent Reference 4 U.S. Pat. No. 3,674,325 Specification
  • the present invention aims at solving the problems found in the above prior art technology.
  • a tappet roller bearing including:
  • a support shaft to be fixed to a locker arm for receiving the movement of a cam to be supported on the cam shaft of an engine
  • first and second rollers respectively supported rotatably on the periphery of the support shaft and arranged in the axial direction of the support shaft, wherein:
  • the first roller constitutes a plain bearing
  • the second roller constitutes a full type roller bearing or a plain bearing.
  • the cam includes a high speed cam and a low speed cam respectively disposed on the cam shaft slidably in the axial direction of the cam shaft;
  • the first roller constituting the plain bearing is contacted with the high speed cam
  • the second roller constituting the full type roller bearing is contacted with the low speed cam.
  • the cam includes a high speed cam and a low speed cam respectively disposed on the cam shaft slidably in the axial direction of the cam shaft;
  • the outer peripheral surface of the first roller to be contacted with the high speed cam is formed by barrel working to be carried out after polish finishing;
  • the outer peripheral surface of the second roller to be contacted with the low speed cam is formed by polish finishing without being barrel worked.
  • the outer peripheral surfaces of the first and second rollers are not crowning worked but have a uniform diameter in the axial direction thereof.
  • At least one of the first and second rollers is structured so that an axial direction end face has a convex shape.
  • the inner roller of the double roller is structured so that an axial direction end face has a convex shape.
  • the second roller constitutes a full type roller bearing
  • the multiple rollers of the roller bearing, together with the second roller, are structured so that respective axial direction end faces have a convex shape.
  • the support shaft is formed to have a staged shape including first and second shaft portions different from each other in the outside diameter dimension thereof;
  • the first roller is disposed on the periphery of the first shaft portion
  • the second roller is disposed on the periphery of the second shaft portion.
  • the first and second rollers are different from each other in the axial direction width thereof.
  • the first and second rollers are different from each other in the roller diameter thereof.
  • a third roller rotatably supported on the periphery of the support shaft and arranged together with the first and second rollers in the axial direction of the support shaft.
  • the third roller is situated on the opposite side to the second roller with respect to the first roller.
  • the outer peripheral surface of at least one of the first to third rollers is crowning worked.
  • the first roller in the first and second rollers which are respectively supported rotatably on the periphery of the support shaft and are arranged together in the axial direction of the support shaft, the first roller constitutes a plain bearing, while the second roller 12 constitutes a full type roller bearing or a plain bearing. Thanks to this structure, the present tappet roller bearing can extend its life, can enhance its assembling efficiency, and can reduce its manufacturing cost.
  • the first roller constituting the plain bearing can be contacted with the high speed cam, while the second roller constituting the full type roller bearing can be contacted with the low speed cam. Thanks to this structure, the present cam follower apparatus can extend its life, can enhance its rotation performance and its assembling efficiency, and can reduce its manufacturing cost.
  • FIG. 1 is a partially cut-away side view of a cam follower apparatus into which a tappet roller bearing according to a first embodiment of the invention is assembled.
  • FIG. 2 is a perspective view of the tappet roller bearing shown in FIG. 1 .
  • FIG. 3 is a section view taken along the A-A arrow line shown in FIG. 1 .
  • FIG. 4 is a perspective view of a tappet roller bearing according to a first modification of the first embodiment of the invention.
  • FIG. 5 is a section view of the tappet roller bearing according to the first modification of the first embodiment of the invention.
  • FIGS. 6A to 6C are respectively section views of the tappet roller bearing according to a second modification of the first embodiment of the invention, showing the combinations of two lines of rollers included therein.
  • FIGS. 7A to 7H are respectively section views of the tappet roller bearing according to a third modification of the first embodiment of the invention, showing the combinations of three lines of rollers included therein.
  • FIGS. 8A to 8E are respectively section views of the tappet roller bearing according to a second embodiment of the invention, showing the combinations of two lines of rollers included therein.
  • FIGS. 9A and 9B are respectively section views of the tappet roller bearing according to the second embodiment of the invention, showing the other combinations of the two lines f rollers included therein.
  • FIGS. 10A and 10B are respectively section views of the tappet roller bearing according to a modification of the second embodiment of the invention, showing the other combinations of the two lines of rollers included therein.
  • FIGS. 11A to 11H are respectively section views of the tappet roller bearing according to a second modification of the second embodiment of the invention, showing the combinations of three lines of rollers included therein.
  • FIGS. 12A to 12C are respectively section views of the tappet roller bearing according to a third modification of the second embodiment of the invention, showing the combinations of three lines of rollers included therein.
  • FIGS. 13A to 13D are respectively section views of the tappet roller bearing according to a fourth modification of the second embodiment of the invention, showing the combinations of three lines of rollers included therein.
  • FIG. 14 is a section view of a tappet roller bearing including two lines of rollers respectively arranged around shafts having different diameters according a third embodiment of the invention.
  • FIGS. 15A to 15C are respectively explanatory views of the tappet roller bearing shown in FIG. 14 , showing the assembling steps of the tappet roller bearing.
  • FIG. 16A is a section view of a modification of the tappet roller bearing of the third embodiment of the invention including two lines of rollers
  • FIG. 16B is a section view of another modification of the tappet roller bearing of the third embodiment of the invention including three lines of rollers.
  • FIG. 17 is a section view of a tappet roller bearing including two lines of rollers having different roller diameters according to a fourth embodiment of the invention.
  • FIG. 18 is a section view of a tappet roller bearing including two lines of rollers having different roller diameters according to a modification of the fourth embodiment of the invention.
  • FIG. 19 is an explanatory side view of a modification of a locker arm.
  • a cam follower apparatus 1 on a cam shaft 2 which can be rotated synchronously with the crank shaft of an engine (not shown), there are respectively supported a high speed cam 3 a and a low speed cam 3 b in such a manner that they can be slid in the axial direction of the cam shaft 2 (in FIG. 1 , in the front and back direction of the sheet of FIG. 1 ). Also, at the position that is disposed opposed to the high speed cam 3 a or low speed cam 3 b slidably in the axial direction thereof, there is arranged a locker arm 4 which is used to receive the movements of these cams 3 a and 3 b.
  • the locker arm 4 has a shaft hole 4 a formed in the longitudinal direction intermediate portion thereof (in FIG. 1 , in the right and left direction), while the lock arm 4 can be rotatably supported on a cylinder head (not shown) through a locker shaft 5 inserted through the shaft hole 4 a.
  • an adjust bolt 6 With the base end portion (in FIG. 1 , the left end portion) of the locker arm 4 , there is threadedly engaged an adjust bolt 6 , while the adjust bolt 6 can be fastened and fixed to such base end portion using a lock nut 6 a. And, with the end portion of the adjust bolt 6 (in FIG. 1 , the lower end portion thereof), there is contacted the end portion (in FIG. 1 , the upper end portion) of an engine valve 7 serving as a suction valve or an exhaust valve supported on a cylinder head (not shown) in such a manner that it can be moved reciprocatingly.
  • the engine valve 7 is always energized by a valve spring 8 in a valve closing direction (a direction where the engine valve 7 is contacted with the adjust bolt 6 ). Therefore, the locker arm 4 is always energized clockwise in FIG. 1 .
  • the tappet roller bearing 10 includes: a first roller 11 and a second roller 12 which are respectively interposed between the paired support wall portions 9 , while the first roller 11 can be contacted with the high speed cam 3 a and second roller 12 can be contacted with the low speed cam 3 b; and, a support shaft 20 the two end portions of which are supported in the shaft holes 9 a of the paired support wall portions 9 and also which supports the first and rollers 11 and 12 rotatably.
  • the support shaft 20 is constituted of a steel-made hollow or solid shaft member and, when the two end portions of the support shaft 20 are caulked into the shaft holes 9 a formed in the paired support wall portions 9 , the support shaft 20 can be fixed to the support wall portions 9 .
  • the first roller 11 with which the high speed cam 3 a can be contacted, constitutes a single roller serving as a plain bearing which can be slidingly contacted with the outer peripheral surface of the support shaft 20 .
  • the second roller 12 with which the low speed cam 3 b can be contacted, constitutes the outer race of a roller bearing including multiple rollers 13 which are interposed in a full type roller manner between the roller bearing and support shaft 20 .
  • the first and second rollers 11 and 12 are substantially equal to each other in the outside diameter dimension thereof.
  • the first and second rollers 11 and 12 may be made of metal such as bearing steel or carbon steel, provided that the metal can secure necessary hardness through the heat treatment thereof. And, they may be constituted of the same material or may be constituted of different materials. For example, by using materials which are different in the carbon contents thereof, they may be prevented from biting into each other.
  • the respective outer peripheral surfaces of the first and second rollers 11 and 12 have been crowning worked, which can prevent an excessive surface pressure due to an edge load from acting on the rolling contact portions of the rollers with the cams 3 a and 3 b and also which makes it possible for the rollers to deal with the inclination of the cams 3 a, 3 b and tappet roller bearing 10 .
  • the crowning may include any of full crowning, partial crowning, logarithmic arc crowning and composite arc crowning.
  • the radius of curvature of the crowning may be different between the first and second rollers 11 and 12 .
  • the radius of curvature of the first roller 11 to be contacted by the high speed cam 3 a may be set smaller than the radius of curvature of the second roller 12 to be contacted by the low speed cam 3 b, and large crowning may be carried out on the first roller 11 with which the high speed cam 3 a can be contacted.
  • the allowable surface pressure of the respective cams 3 a and 3 b is up to 2 GPa or so, while the allowable surface pressure of the tappet roller bearing 10 is set higher than the allowable surface pressure of the respective cams 3 a and 3 b.
  • the crowning working is carried out on the outer peripheral surfaces of the cams 3 a and 3 b in order to prevent their respective contact surface pressures from exceeding their respective allowable surface pressures.
  • the crowning working can be omitted.
  • the outer peripheral surfaces of the first and second rollers 11 and 12 respectively have a uniform diameter in the axial direction thereof.
  • the second roller 12 to be contacted by the low speed cam 3 b, after it is polish finished, may not receive additional surface working such as barrel working.
  • additional surface working such as barrel working.
  • the first roller 11 to be contacted by the high speed cam 3 a there are carried out not only polish finishing but also additional surface working such as barrel working.
  • FIG. 2 and also in FIGS. 4 , 6 , 7 and the like which will be described later, the illustration of the support wall portion 9 for supporting the support shaft 20 is omitted.
  • the outer peripheral surface of the first or second roller 11 or 12 is contacted with the outer peripheral surface of the high speed cam 3 a or low speed cam 3 b due to the energizing force of the valve spring 8 .
  • the rotation of the cam shaft 2 is converted to the reciprocating oscillatory motion of the locker arm 4 about the locker shaft 5 , and the engine valve 7 is moved or reciprocated in the axial direction thereof against the energizing force of the valve spring 8 or due to the energizing force of the valve spring 8 , while the lift amount of the engine valve 7 is variable. Thanks to this, a suction port or an exhaust port to be formed in a cylinder head (not shown) can be opened and closed.
  • the tappet roller bearing 10 since the first roller 11 is used as a plain bearing and the second roller 12 is used a roller bearing, there is eliminated the need to provide a washer, which is necessary when the two rollers are respectively constituted of roller bearings, for prevention of mutual interference between the two rollers in the axial direction thereof. Therefore, the tappet roller bearing 10 is enhanced in the assembling efficiency thereof and also can reduce the manufacturing cost thereof.
  • a plain bearing has a problem that it has such sufficient durability as can neglect the need to consider the life of the bearing but it provides large frictional resistance in the low speed rotation area.
  • the frictional resistance of the plain bearing is low and is substantially equal to that of a roller bearing.
  • the second roller 12 for contact with the low speed cam 3 b is constituted of a roller bearing to thereby be able to reduce the frictional resistance in the low speed rotation time
  • the first roller 11 for contact with the high speed cam 3 a is constituted of a plain bearing to thereby be able to eliminate a possibility that a high load in the high speed rotation time can have an influence on the life of the bearing.
  • the first and second rollers 11 and 12 are structured as in the present embodiment according to the high speed cam 3 a and low speed cam 3 b, the enhanced rotation performance (dynamic torque) due to the reduced frictional resistance and the increased life of the bearing can be attained at the same time.
  • FIGS. 4 and 5 respectively show a tappet roller bearing 10 according to a modification of the present embodiment.
  • a first roller 11 a constitutes the outer roller of a double roller (plain bearing) including an inner roller 14 which is interposed between a support shaft 20 and first roller 11 a.
  • the first roller 11 a functions as an outer roller and cooperates together with the inner roller 14 to constitute a double roller in this manner, when compared with the single roller 11 according to the first embodiment, the frictional resistance can be reduced.
  • FIGS. 6 and 7 respectively show another modification of the tappet roller bearing according to the first embodiment.
  • the tappet roller bearing can be structured with no provision of a washer.
  • the first and second rollers 11 and 12 a may be respectively constituted of plain bearings formed as single rollers; as shown in FIG. 6B , the first roller 11 a may be constituted of a double roller including an inner roller 14 , and the second roller 12 may be constituted of a single roller; and, as shown in FIG. 6C , the first and second rollers 11 a and 12 b may be both constituted of double rollers respectively including inner rollers 14 and 15 .
  • the materials of the first and second rollers 11 a, 12 b and inner rollers 14 , 15 may be changed respectively.
  • the tappet roller bearing 10 may further include a third roller 16 , 16 a, 16 b which is rotatably supported on the periphery of a support shaft 20 and is arranged in the axial direction of the support shaft 20 together with the first and second rollers 11 , 12 .
  • the types of the rollers to be arranged on both sides in the axial direction of the support shaft 20 may be the same.
  • the third roller 16 , 16 a is constituted of a plain bearing
  • the second roller 12 , 12 a, 12 b may be constituted of a full type roller bearing or may be constituted of a plain bearing. In this case, it is unnecessary to consider interference between the rollers and unnecessary to dispose a washer.
  • the third roller 16 b in the case that the third roller 16 b is constituted of a full type roller bearing and the second roller 12 is also constituted of a full type roller bearing, in order that interference between the rollers can be prevented without provision of a washer, the third roller 16 b may be arranged such that it is situated on the opposite side to the second roller 12 with respect to the first roller 11 , 11 a, that is, the third roller 16 b and second roller 12 may be arranged on both sides in the axial direction of the support shaft 20 .
  • a tappet roller bearing according to a second embodiment of the invention with reference to FIGS. 8 ⁇ 13 .
  • the single roller itself may also be referred to as the composing element of the bearing;
  • the outer roller and inner roller may also be referred to as the composing elements of the bearing; and, in the case of a full type roller bearing, the roller constituting the outer race and multiple rollers may also be referred to as the composing elements of the bearing.
  • the axial direction two end faces of at least first and second rollers 11 , 11 a and 12 , 12 a are formed to have a convex shape.
  • bearings which are respectively constituted of the first and second rollers 11 , 11 a, 12 , 12 a, can be prevented from moving together, thereby being able to reduce sliding torque which can be generated between the mutually opposing end faces of the rollers.
  • supply of a lubricant to the support shaft 20 can be facilitated and thus the support shaft 20 can be prevented against abrasion and seizure.
  • the above structure according to the present embodiment can be applied to an arbitrary tappet roller bearing 10 according to the first embodiment. That is, for example, similarly to FIG. 3 , in a tappet roller 10 shown in FIG. 8A in which a first roller 11 constitutes a single roller and a second roller 12 constitutes a full type roller bearing, the axial direction two end faces of the second roller 12 and multiple rollers 13 are respectively formed to have a convex shape (a convex-shaped partially spherical surface).
  • a tappet roller bearing 10 as well which is shown in FIG. 8B and in which a first roller 11 a constitutes the outer roller of a double roller and a second roller 12 constitutes a full type roller bearing, the axial direction two end faces of the second roller 12 and multiple rollers 13 are formed to have a convex shape (a convex-shaped partially spherical surface).
  • FIGS. 8C ⁇ 8E similarly to FIGS. 6A ⁇ 6C , respectively show a structure in which, in the case that first and second rollers 11 , 11 a, 12 a, 12 b are both constituted of a plain bearing, the axial direction end faces of one of the first and second rollers are respectively formed to have a convex shape.
  • the tappet roller bearing 10 is constituted of a single roller and a double roller, in order to prevent the mutually opposing axial direction end faces of the rollers from surface contacting with each other, preferably, the axial direction two end faces of the inner and outer rollers of the double roller may be respectively formed to have a convex shape.
  • FIGS. 8A ⁇ 8E there is shown a structure in which the axial direction two end faces of one of the first and second rollers 11 , 11 a, 12 a, 12 b are respectively formed to have a convex shape
  • the axial direction two end faces of both the first and second rollers 11 , 11 a, 12 a, 12 b may also be respectively formed to have a convex shape. That is, as shown in FIG. 9A , in a tappet roller bearing having a similar structure to FIG.
  • the axial direction two end faces of the first roller 11 a (the outer roller of the double roller) and inner roller 14 as well as the axial direction two end faces of the second roller 12 and multiple rollers 13 are respectively formed to have a convex shape (a convex-shaped partially spherical surface).
  • the axial direction two end faces of first and second rollers 11 and 12 a respectively constituting a single roller are formed to have a convex shape.
  • the structure according to the present embodiment can also be applied to a structure including a third roller 16 , 16 a constituted of a full type roller bearing or a plain bearing. That is, a second roller 12 and multiple rollers 13 respectively constituting a full type roller bearing, first or second roller 11 or 12 a constituting a single roller, first or second roller 11 a or 12 b constituting the outer roller of a double roller and inner roller 14 or 15 of the double roller, which are respectively situated in the axial direction intermediate portion of the tappet roller bearing in FIGS. 11A ⁇ 11H , are respectively formed such that the axial direction two end faces thereof respectively have a convex shape. Or, as shown in FIGS.
  • a convex shape may also be formed in the axial direction two end faces of two bearing composing elements respectively situated on both sides in the axial direction of the support shaft 20 .
  • a convex shape may also be formed in the axial direction two end faces of three bearing composing elements.
  • the second roller 12 a shown in FIG. 11F and the first roller 11 shown in FIG. 11H respectively have a convex-shaped axial direction end faces which are similar to the FIG. 11B .
  • a structure which can prevent a tappet roller bearing 10 against wrong assembly when it is assembled.
  • first and second rollers 11 , 11 a, 12 , 12 a, 12 b are different from each other in the surface treatment thereof, even when they respectively constitute the same bearing composing elements, it is necessary to judge whether they are to be contacted with the high speed or low speed cam, which makes it necessary to take measures against wrong assembly.
  • a support shaft 20 is formed to have a staged shape including a first shaft portion 20 a and a second shaft portion 20 b respectively adjoining each other and having different outside diameter dimensions.
  • the first roller 11 is disposed on the periphery of the first shaft portion 20 a, while the second roller 12 is disposed on the periphery of the second shaft portion 20 b.
  • the second roller 12 to be contacted with the low speed cam 3 b is disposed on the periphery of the second shaft portion 20 b having a smaller diameter than the first shaft portion 20 a.
  • the outside diameter dimensions of the first and second rollers 11 and 12 are set equal to each other. Therefore, the sum of the diameter direction dimension (thickness) of the second roller 12 and the diameter direction dimension (roller diameter) of multiple rollers 13 can be set larger than the diameter direction dimension (thickness) of the first roller 11 .
  • the thickness of the second roller 12 may be set larger than the roller diameter.
  • the tappet roller bearing 10 shown in FIG. 14 is assembled to the locker arm 4 using a method shown in FIG. 15 .
  • the tappet roller bearing 10 is held by a staged stop plug 50 including a shaft portion having an outside diameter substantially equal to the axial direction width of the tappet roller bearing 10 and also substantially equal to the first and second shaft portions 20 a, 20 b of the support shaft 20 .
  • the tappet roller bearing 10 while it remains held by the stop plug 50 , is interposed between the support wall portions 9 of the locker arm 4 ; and, the stop plug 50 is pushed out from the small diameter side thereof using a jig 51 having an outside diameter dimension substantially equal to the small diameter side outside diameter of the stop plug 50 .
  • the support shaft 20 is inserted from the side where the stop plug 50 has been pushed out to thereby remove the jig 51 , so that the tappet roller bearing 10 is assembled to the locker arm 4 without wrong assembly.
  • the first and second rollers 11 and 12 may be formed such that they are different from each other in the axial direction width thereof, thereby being able to visually prevent the wrong assembly of the tappet roller bearing 10 . That is, as shown in FIG. 16A , the axial direction width a of the first roller 11 receiving a large load from the high speed cam 3 a may be formed set larger than the axial direction width b of the second roller 12 .
  • the tappet roller bearing 10 is constituted of a combination of a plain bearing including the first roller 11 constituting a single roller and a full type roller bearing including the second and third rollers 12 and 16 b constituting the outer race of the roller bearing
  • the axial direction width a of the first roller 11 may also be set larger than the axial direction width b of the second and third rollers 12 and 16 b.
  • the tappet roller bearing may also be structured such that the first and second rollers 11 and 12 are formed different from each other in the roller diameter thereof, whereby the wrong assembly of the tappet roller bearing can be prevented visually.
  • the roller diameter of the first roller 11 is set larger than that of the second roller 12 to thereby reduce the surface pressure.
  • the roller diameter of the second roller 12 may be increased.
  • the tappet roller bearing may also be structured by combining together the two structures respectively shown in FIGS. 14 and 17 . That is, the support shaft 20 is formed to have a staged shape which includes first and second shaft portions 20 a and 20 b respectively having mutually different outside diameter dimensions, the first roller 11 is disposed on the periphery of the first shaft portion 20 a, while the second roller 12 is disposed on the periphery of the second shaft portion 20 b. Also, the first and second rollers 11 and 12 are structured such that their respective roller diameters (outside diameters) are different from each other.
  • both bearings are constituted of plain bearings and, there can also be employed in a structure which includes such first to third rollers as shown in FIG. 7 .
  • a structure in which rollers are respectively disposed in the shaft portions of the support shaft 20 having different axial diameters and, a structure in which rollers are formed such that their respective axial direction widths are different from each other.
  • a structure in which the axial direction widths of the respective rollers are different from each other can be applied to any of the above embodiments.
  • at least one of the rollers may also be formed to have a roller diameter which is different from the roller diameters of the remaining rollers.
  • the tappet roller bearing 10 is mounted on the leading end portion of the locker arm 4 .
  • the tappet roller bearing 10 may also be mounted onto the intermediate portion of a locker arm 40 .
  • the locker arm 40 includes a shaft hole 41 which is formed in the intermediate portion of the locker arm 40 and to the inner surface of which the two end portions of the support shaft 20 of the tappet roller bearing 10 can be fitted and fixed.
  • the invention is based on the Japanese Patent Application (Patent Application No. 2010-055650) filed on Mar. 12, 2010 and the Japanese Patent Application (Patent Application No. 2011-006244) filed on Jan. 14, 2011 and thus the contents thereof are incorporated herein for reference.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US13/060,206 2010-03-12 2011-01-18 Tappet roller bearing Abandoned US20120318216A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2010-055650 2010-03-12
JP2010055650 2010-03-12
JP2011006244A JP2011208631A (ja) 2010-03-12 2011-01-14 タペットローラ軸受
JP2011-006244 2011-01-14
PCT/JP2011/050763 WO2011111418A1 (ja) 2010-03-12 2011-01-18 タペットローラ軸受

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US13/060,206 Abandoned US20120318216A1 (en) 2010-03-12 2011-01-18 Tappet roller bearing

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US (1) US20120318216A1 (zh)
EP (1) EP2546480A4 (zh)
JP (1) JP2011208631A (zh)
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US20160215889A1 (en) * 2015-01-26 2016-07-28 Hamilton Sundstrand Corporation Butterfly valve with modified scotch yoke connection
DE102017104641A1 (de) 2017-03-06 2018-09-06 Thyssenkrupp Ag Nockenfolgerrolle, Nockenfolger, Ventiltrieb und Brennkraftmaschine
US10533463B1 (en) * 2018-09-06 2020-01-14 Delphi Technologies Ip Limited Switchable rocker arm and roller retainer thereof
US10544711B1 (en) * 2018-09-06 2020-01-28 Delphi Technologies Ip Limited Switchable rocker arm and roller retainer thereof

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DE102012219506A1 (de) * 2012-10-02 2014-04-03 Schaeffler Technologies Gmbh & Co. Kg Hebelartiger Nockenfolger
CN107923268B (zh) * 2015-08-19 2020-10-20 沃尔沃卡车集团 可变气门促动机构、内燃发动机和车辆
DE102015118884A1 (de) * 2015-11-04 2017-05-04 Pierburg Gmbh Mechanisch steuerbarer Ventiltrieb
US10697493B2 (en) 2018-02-15 2020-06-30 Roller Bearing Company Of America, Inc. Cam follower with multiple rows of independently operating bearings
CN108533616B (zh) * 2018-06-20 2020-10-23 安徽航睿电子科技有限公司 一种低速重载荷滚珠轴承

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160215889A1 (en) * 2015-01-26 2016-07-28 Hamilton Sundstrand Corporation Butterfly valve with modified scotch yoke connection
US10088056B2 (en) * 2015-01-26 2018-10-02 Hamilton Sundstrand Corporation Butterfly valve with modified scotch yoke connection
DE102017104641A1 (de) 2017-03-06 2018-09-06 Thyssenkrupp Ag Nockenfolgerrolle, Nockenfolger, Ventiltrieb und Brennkraftmaschine
US10533463B1 (en) * 2018-09-06 2020-01-14 Delphi Technologies Ip Limited Switchable rocker arm and roller retainer thereof
US10544711B1 (en) * 2018-09-06 2020-01-28 Delphi Technologies Ip Limited Switchable rocker arm and roller retainer thereof

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EP2546480A4 (en) 2014-06-25
JP2011208631A (ja) 2011-10-20
WO2011111418A1 (ja) 2011-09-15
CN102292523A (zh) 2011-12-21

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