EP2806117A1 - Cam follower device - Google Patents

Cam follower device Download PDF

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Publication number
EP2806117A1
EP2806117A1 EP12865748.3A EP12865748A EP2806117A1 EP 2806117 A1 EP2806117 A1 EP 2806117A1 EP 12865748 A EP12865748 A EP 12865748A EP 2806117 A1 EP2806117 A1 EP 2806117A1
Authority
EP
European Patent Office
Prior art keywords
support
support shaft
inner ring
wall sections
circumferential surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12865748.3A
Other languages
German (de)
English (en)
French (fr)
Inventor
Hiroshi Noda
Satoshi Hachisuka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Publication of EP2806117A1 publication Critical patent/EP2806117A1/en
Withdrawn legal-status Critical Current

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Classifications

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

Definitions

  • the present invention relates to a cam follower apparatus that is assembled in a valve mechanism in the engine of an automobile and the like
  • FIG 12 and FIG. 13 illustrate an example of conventional construction of a cam follower apparatus as disclosed in JP 2006-183856 (A )
  • a rocker arm 1, which is the main part of the cam follower apparatus is supported so as to be able to rotate freely by the cylinder head (not illustrated in the figure) of the engine by way of a rocker shaft 3 that is inserted into a shaft hole 2 that is formed in the middle section in the lengthwise direction thereof.
  • an adjustment bolt 4 is fastened the base end section of the rocker arm 1.
  • the base end surface (top end surface in FIG 12 ) of an engine valve 6, which is an air-intake valve or exhaust valve, that is supported by the cylinder head so as to be able to move back-and-forth comes in contact with the tip-end surface (bottom surface in FIG. 12 ) of the adjustment bolt 4.
  • the engine valve 6 is always forced by a return spring 7 in closed-valve direction (direction of contact with the adjustment bolt 4). Therefore, an elastic force in the clockwise direction around the rocker shaft 3 in FIG 12 is applied to the rocker arm 1.
  • a tappet roller 8 is supported on the tip-end section (right end section in FIG 12 ) of the rocker arm 1 by way of a support shaft 9 so as to be able to rotate freely, and the outer circumferential surface of the tappet roller 8 comes in contact with the outer circumferential surface of the cam 10 due to the elastic force of the return spring 7.
  • a cam 10 is integrally formed with a camshaft 11 that rotates in conjunction with the crankshaft (not illustrated in the figure) and is supported by the cylinder head so as to be able to rotate freely.
  • the portion that supports the tappet roller 8 by way of the support shaft 9 so as to be able to rotate freely with respect to the rocker arm 1 is constructed as illustrated in FIG 13 .
  • the support arm 9 spans between a pair of support wall sections 12 that are provided on the tip-end section of the rocker arm 1 so as to be parallel with each other and separated by a space.
  • the tappet roller 8 is supported by a radial roller (needle) bearing 14 that comprises a plurality of cylindrical rollers (needles) 13 so as to be able to rotate freely around a portion in the middle section of the support shaft 9 that is located between the inside surfaces of the support wall sections 12.
  • Both end sections of the support shaft 9 fit inside and are supported by circular support holes 15 that are provided in the support wall sections 12 so as to be concentric with each other.
  • the support shaft 9 is firmly connected and fastened to the support holes 15.
  • JP 2009-079569 discloses construction in which a tappet roller 8a is supported by a radial roller bearing 14 so as to be able to rotate freely around a support shaft 9a that is fastened to the middle section in the lengthwise direction of the rocker arm 1a.
  • Both end section of the support shaft 9a are fitted inside and supported by circular support holes 15a that are provided in a pair of support wall sections 12 so as to be concentric with each other.
  • the tip-end section of a lash adjuster which is the fulcrum, comes in contact with one surface on one end section (bottom surface on the left end section in FIG. 14 and FIG. 15 ) of the rocker arm 1a, and the base end surface of the engine value comes in contact with one surface on the other end section (bottom surface of the right end section in FIG. 14 and FIG 15 )
  • the outer circumferential surface in the middle section of the support shaft 9 (9a) functions as an inner-ring raceway of the radial roller bearing 14 for supporting the tappet roller 8 (8a) so as to be able to rotate freely, so preferably this outer circumferential surface in the middle section will not be damaged.
  • construction in which the support shaft 9 (9a) is press fitted into the support holes 15 (15a) that are formed in the support wall sections 12 (12a) is disadvantageous from the aspect of preventing damage.
  • a full complement roller bearing that does not have a cage is used as the radial roller bearing that is provided between the inner circumferential surface of the tappet roller 8 (8a) and the outer circumferential surface in the middle section of the support shaft 9 (9a).
  • a roller assembly in which a plurality of cylindrical rollers are arranged is assembled in the space between the inner circumferential surface of the tappet roller 8 (8a) and the outer circumferential surface of a shaft member (detent plug) that is located on the inner-diameter side of the tappet roller 8 (8a).
  • the roller assembly is placed between the inside surfaces in the width direction of the support wall sections 12 (12a) with both end surfaces of the detent plug and the support holes 15 (15a) in the support wall sections 12 (12a) in an aligned state.
  • the support shaft 9 (9a) is inserted from the outside in the axial direction of one of the support wall sections 12 (12a) into the support hole 15 (15a) of one support wall section 12 (12a) of the support wall sections 12 (12a). Then, while pressing the detent plug with the support shaft 9 (a), the support shaft 9 (9a) is inserted until one end section thereof is inserted into the support hole 15 (15a) in the other support wall section 12 (12a).
  • both end section of the support shaft 9 (9a) are crimped and expanded In this state, the support shaft 9 (9a) is supported in a state wherein relative rotation with respect to the support wall sections 12 (12a) is prevented.
  • the work of inserting the support shaft 9 (9a) into the inner-diameter side of the tappet roller 8 (8a) while pressing the detent plug is troublesome.
  • the number of parts for assembly and the number of assembly steps increase because of the use of the detent plug, so the cost increase.
  • the outer diameter of the support shaft 9 (9a) and the inner diameter of the support holes 15 (15a) in the support wall sections 12 (12a) are set based on the diameter of the inscribed circle of the cylindrical rollers 13 of the radial roller bearing 14. Therefore, the freedom of design of the support shaft 9 (9a) and the support wall sections 12 (12a) is low Furthermore, when the diameter of the inscribed circle of the cylindrical rollers 13 of the radial roller bearing 14 is large, it is necessary to make the overall diameter of the support shaft 9 (9a) large in order to correspond to the diameter of the inscribed circle. Due to this, the weight thereof may be increased.
  • the support shaft 9 (9a) is supported in a state wherein relative rotation with respect to the support wall sections 12 (12a) is prevented, so load zone of the support shaft 9 (9a) is limited to a fixed range.
  • radial loads that are applied during use are always applied (supported) in the same location of the support shaft 9 (9a)
  • repeated loading is applied to the portion of the support shaft 9 (9a) where radial loading is applied, and there is a possibility of a decrease in durability
  • cam follower apparatus that has excellent durability, assembly characteristics, and freedom of design, is capable of being made compact and lightweight, and is capable of reducing the manufacturing cost thereof.
  • the cam follower apparatus of the present invention has a rocker arm, a support shaft, an inner ring member and a tappet roller.
  • the rocker arm has a pair of support wall sections that are provided so as to be separated from each other by a space, and a pair of support holes that are formed in positions in these support wall sections that are aligned with each other, and is provided so as to face a cam that is fastened to a camshaft that rotates in synchronization with the crankshaft of an engine and oscillates and displaces according to the motion of this cam.
  • the support shaft with both ends sections thereof inserted in the pair of support holes, spans between the pair of support wall sections and is supported by the support wall sections.
  • the inner ring member has an outer diameter that is larger than the inner diameter of the support holes, and fits with an interference fit onto the middle section in the axial direction of the support shaft in a state such that relative rotation with respect to the support shaft is prevented Furthermore, the tappet roller is arranged around the inner ring member so as to be able to rotate relative to the inner ring member.
  • both end sections of the support shaft fit with a loose fit inside the pair of support holes so as to be able to rotate on the inside of the support holes
  • a radial roller bearing is provided between the inner circumferential surface of the tappet roller and the outer circumferential surface of the inner ring member.
  • the radial roller bearing be a full complement roller bearing that does not have a cage
  • a pair of circular ring shaped washers are provided on the inside in the width direction of the pair of support wall sections so as to cover the opening sections on both ends of a bearing space of the radial roller bearing
  • the outer diameter of the washers is greater than the dimension in the height direction of the support wall sections
  • An improvement in durability is due to performing hardening of the entire support shaft by immersion quenching.
  • it is not necessary to crimp both end sections of the support shaft, so it is possible hardening of the support shaft by immersion quenching
  • it is possible to maintain sufficient strength and rigidity of the entire support shaft, and to effectively prevent the support shaft from plastically deforming due to radial loading during use.
  • the load zone of the support shaft is not limited to a fixed range.
  • Improvement of the assembly characteristics is made possible by providing the inner ring member
  • a roller assembly in which an inner ring member, tappet roller and other components (for example, cylindrical rollers of a radial roller bearing) are assembled arranged between the support wall sections, it is possible to perform assembly by inserting the support shaft in order through the support hole of one support wall section, the inner circumferential surface of the inner ring member and the support hole of the other support wall section Therefore, there is no need to assemble the support shaft by inserting and pressing out a detent plug that was located on the inside of the tappet roller as was done in the conventional construction
  • the outer diameter of the inner ring member can be appropriately set to correspond to the diameter of the inscribed circle of the cylindrical rollers of the radial roller bearing, and to set the inner diameter of the inner ring member to correspond with the outer diameter of the support shaft and the inner diameter of the support holes in the support wall sections.
  • Reduction in the size and weight is also made possible by providing the inner ring member.
  • the inner diameter of the inner ring member it is possible to reduce the outer diameter of the support shaft, so together with being able to keep the width dimension around the support holes in the support wall sections in the radial direction of the support holes at a fixed width, it is possible to reduce the dimension in the height direction of the support wall sections As a result, it is possible to maintain a desired rigidity, and to reduce the size and weight of the support wall sections and the entire rocker arm.
  • these washers are able to prevent the cylindrical rollers of the radial roller bearing from coming out in the axial direction from the bearing space, so it is possible to further reduce the dimension in the height direction of the support wall sections.
  • FIG. 1 illustrates a first example of an embodiment of the present invention.
  • Features of the cam follower apparatus of the present invention are the construction of support wall sections 12b, 12c that support a support shaft 9b, and providing an inner ring 16, which is an inner-ring member, between the support shaft 9b and the tappet roller 8b.
  • the construction of the cam follower apparatus other than that of the features of the present invention, and the assembled state in an engine is the same as in conventional construction, including that illustrated in FIG. 12 to FIG 15 , so an explanation thereof is omitted or simplified, so that explanation below centers on the features of this example
  • the cam follower apparatus of this example has a rocker arm 1b, a support shaft 9b, an inner ring 16, which is an inner-ring member, a tappet roller 8a and a plurality of cylindrical rollers 13.
  • the rocker arm 1b has a pair of support wall sections 12b, 12c that are provided in a state being separated by an interval from each other, and a pair of support holes 15b 15c is formed in positions in these support wall sections 12b, 12c that are aligned with each other
  • both end sections of a hollow or solid steel support shaft 9b are inserted into support holes 15b, 15c in steel support wall sections 12b, 12c by way of a minute gap (loose fit), and by spanning between the support wall sections 12b, 12c, the support shaft 9b is supported such that relative rotation with respect to the support wall sections 12b, 12c is possible.
  • the outer diameter D 9 of the support shaft 9b is a little less than the inner diameter d 15 of the support holes 15
  • the support shaft 9b is entirely hardened by immersion quenching in which the entire support shaft 9b is heated and immersed in quenching oil.
  • immersion quenching the processing cost becomes high, however, it is also possible to harden the support shaft 9b by induction hardening in which in the outer circumferential surface in the middle section is hardened and raw portion remain on both end sections of the support shaft 9b.
  • a cylindrical shaped inner ring 16 is fitted onto the outer circumferential surface of the middle section in the axial direction of the support shaft 9b with an interference fit so as to be prevented from relative rotation with respect to the support shaft 9b (state in which it is possible to rotate together with the support shaft 9b).
  • the outer diameter D 16 of the inner ring 16 is greater than the inner diameter d 15 of the support holes 15b, 15c (D 36 > d 15 ).
  • An inner-ring raceway 17 is formed around the outer circumferential surface of the inner ring 16. Moreover, a tappet roller 8b is arranged concentrically around (on the outer diameter side of) the inner ring 16 such that relative rotation with respect to the inner ring 16 is possible. An outer-ring raceway 18 is formed around the inner circumferential surface of the tappet roller 8b A radial roller bearing 14a is formed by arranging a plurality of cylindrical rollers 13 between the inner-ring raceway 17 and the outer-ring raceway 18. In this example, the radial roller bearing 14a is composed of a full complement roller bearing in which no cage is provided, however, it is also possible to use cylindrical rollers with a cage as the cylindrical rollers.
  • a roller assembly 19 in which the plurality of cylindrical rollers 13 are arranged is assembled in the space (bearing space 21) between the inner circumferential surface of the tappet roller 8b and the outer circumferential surface of the inner ring 16 that is provide on the inner-diameter side of the tappet roller 8b.
  • the roller assembly 19 is placed between the inside surfaces in the width direction of the support wall sections 12b, 12c in a state where the opening sections on both end sections in the axial direction of the inner circumferential surface of the inner ring 16 and the support holes 15b, 15c in the support wall sections 12b, 12c are aligned.
  • the support shaft 9b is inserted through the support hole 15b in one support wall section 12b of the support wall sections 12b, 12c from the outside in the width direction of that one support wall section 12b. While pressing the inner circumferential surface of the inner ring 16, the support shaft 9b is further pressed until one end section thereof (left end section in FIG. 1 ) is inserted into the support hole 15c in the other support wall section 12c. In this state, a minute gap is provided between the outer circumferential surface of both end sections of the support shaft 9b and the inner circumferential surface of the support holes 15b, 15c in the support wall sections 12b, 12c.
  • the assembly direction for assembling the support shaft 9b can also be the opposite direction.
  • maintaining durability is achieved by performing a hardening process using immersion quenching on the entire support shaft 9b.
  • the cam follower apparatus of the present invention by making the outer diameter D 16 of the inner ring 16 greater than the inner diameter d 15 of the support holes 15b, 15c in the support wall sections 12b, 12c, it is possible to prevent the support shaft 9b from coming out in the axial direction with respect to the support wall sections 12b, 12c Therefore, it is not necessary to crimp both end sections of the support shaft 9b, and it is also not necessary to keep both end sections of the support shaft 9b in the raw state (state in which hardening is not performed).
  • the support shaft 9b is supported in a state so as to be able rotate relative to the support wall sections 12b, 12c. Therefore, the load zone of the support shaft 9b is not limited to a fixed range. In other words, the location on the support shaft 9b where the radial load is applied during use is not always the same. As a result, it is possible to prevent repeated loading to the same location on the support shaft 9b, and thus it is possible to increase the life of the support shaft 9b.
  • improvement of the assembly characteristics is due to providing the inner ring 16.
  • the roller assembly 19 arranged between the support wall sections 12b, 12c, it is possible to assemble the support shaft 9b by inserting the support shaft in order through the support hole 15b in one support wall section 12b, the inner circumferential surface of the inner ring 16 and the support hole 15c in the other support wall section 12c. Therefore, work to push a detent plug that is arranged on the inner-diameter side of the tappet roller 8 (8a) (see FIG. 12 to FIG 15 ) out by pressing the support shaft while inserting it thereinto as was done in the conventional construction is not necessary.
  • the outer diameter of the support shaft 9 (9a) and the inner diameter of the support holes 15 (15a) in the support wall sections 12 (12a) are regulated by the diameter of the inscribed circle of the cylindrical rollers of the radial roller bearing 14.
  • the support shaft 3a and support wall sections 4a, 4b can be made more compact as the freedom of design improves in this way, it is possible to improve the lubrication performance of the radial roller bearing 14a.
  • the dimension H 12 in the height direction of the support wall sections 12b, 12c can be reduced, and it is possible to reduce the area of overlapping portions with respect to the axial direction between the inside surfaces in the width direction of the support wall sections 12b, 12c and both end surfaces in the axial direction of the tappet roller 8b.
  • the hardening process for hardening the support shaft 9b is performed by immersion quenching, which is lower in cost than induction hardening. Furthermore, there is no need for a detent plug during assembly As a result of these, it is possible to reduce the processing cost and parts cost, as well as it is possible to reduce the overall manufacturing cost of the cam follower apparatus.
  • FIG 2 illustrates a second example of an embodiment of the present invention.
  • the outer circumferential surface of the inner ring 16a that is fitted around the outer circumferential surface of the middle section in the axial direction of the support shaft 9b comes in sliding contact with the inner circumferential surface of the tappet roller 8b that is provided in a state so as to be able to rotate relative to the inner ring 16a.
  • the shape and dimensions of the tappet roller 8b are the same as in the first example of an embodiment.
  • the cam follower apparatus of this example has so-called double roller construction in which the radial roller bearing 14a in the first example of an embodiment is omitted
  • the inner ring 16a of the cam follower apparatus of this example is similar to the inner ring 16 of the first example of an embodiment in that the inner ring 16a fits with an interference fit around the outer circumferential surface of the middle section in the axial direction of the support shaft 9b in a state so as to be able to rotate together with the support shaft 9b (prevented from relative rotation with respect to the support shaft 9b) Therefore, from a functional aspect, the cam follower apparatus of this example functions as a so-called single-roller cam follower apparatus.
  • the other construction, functions and effects of this example are the same as in the first example of an embodiment.
  • FIG 3 illustrates a third example of an embodiment of the present invention.
  • an inner-diameter side roller 20 which is a cylindrical member, is provided between the outer circumferential surface of the inner ring 16 that is fitted around the outer circumferential surface of the middle section in the axial direction of the support shaft 9b and the inner circumferential surface of the tappet roller 8b in a state so as to be able to rotate relative to the inner ring 16 and the tappet roller 8b.
  • the shape and dimensions of the tappet roller 8b and inner ring 16 are the same as in the first example of an embodiment.
  • the cam follower apparatus of this example has so-called triple roller construction in which an inner-diameter side roller 20 is provided instead of the radial roller bearing 14a of the first example of an embodiment
  • the inner ring 16 of the cam follower apparatus of this example is fitted around the outer middle section in the axial direction of the support shaft 9b in a state such that relative rotation with respect to the support shaft 9b is prevented (rotation with the support shaft 9b is possible). Therefore, from a functional aspect, the cam follower apparatus of this example functions as a so-called double roller cam follower apparatus.
  • the other construction, functions and effects of this example are the same as in the first example of an embodiment
  • FIG 4 and FIG. 5 illustrate a fourth example of an embodiment of the present invention.
  • a pair of circular ring shaped washers 22 made using a hard metal or a synthetic resin is provided in the axial direction between the inside surfaces in the width direction of the pair of support wall sections 12d, 12e and both end surfaces in the axial direction of the inner ring 16.
  • the outer diameter D 22 of the washers 22 is greater than the inner diameter d 8 of the tappet roller 8b (D 22 > d 8 ).
  • the washers 22 are provided in a state so as to cover the opening sections on both ends in the axial direction of the bearing space 21 where the cylindrical rollers 13 of the radial roller bearing 14a are located.
  • the diameter D 22 of the washers 22 is greater than the dimension H 12d in the height direction (up-down direction in FIG 4 and FIG. 5 ) of the support wall sections 12d, 12e (D 22 > H 12d ).
  • the washers 22 cover the opening sections on both ends in the axial direction of the bearing space 21. Therefore, wear due to the inside surfaces in the width direction of the support wall sections 12d, 12e rubbing against the rollers 13 of the radical roller bearing 14a is prevented, and thus it is possible to increase the life of the support wall sections 12d, 12e.
  • the other construction, functions and effects of this example are the same as in the first example of an embodiment.
  • FIG 6 and FIG. 7 illustrate a fifth example of an embodiment of the present invention.
  • the dimension L 16b in the axial direction of the inner ring 16b is larger than the dimension L 16 in the axial direction of the inner ring 16 (see FIG 1 ) of the first example of an embodiment (L 16b > L 16 ).
  • the shape and dimensions of the tappet roller 8b are the same as in the first example of an embodiment. Therefore, both end sections in the axial direction of the inner ring 16b are located further on the outside in the width direction than both end sections in the axial direction of the tappet roller 8b.
  • a pair of circular ring shaped washers 22a are provided on both end sections in the axial direction of the outer circumferential surface of the inner ring 16b (portions further on the outside in the width direction than both end surfaces in the axial direction of the tappet roller 8b).
  • the outer diameter D 22a of the washers 22a is larger than the inner diameter d 8 of the tappet roller 8b (D 22a > d 8 ) Therefore, the washers 22a are provided in a state so as to cover the opening sections on both ends in the axial direction of the bearing space 21 in which the cylindrical rollers 13 of the radial roller bearing 14b are located
  • the outer diameter D 22a of the washers 22a is larger than the dimension H 12d in the height direction (up-down direction in FIGS. 6 and 7 ) of the support wall sections 12d, 12e (D 22a > H 12d ).
  • the other construction, functions and effect of this example are the same as in the fourth example of an embodiment.
  • FIG. 8 and FIG. 9 illustrate a sixth example of an embodiment of the present invention
  • the dimension L 8c in the axial direction of the tappet roller 8c is greater than the dimension L 8 in the axial direction of the tappet roller 8b in the first example of an embodiment (L 8c > L 8 )
  • the shape and dimensions of the inner ring 16 are the same as in the first example of an embodiment Therefore, both end sections in the axial direction of the tappet roller 8c are located further on the outside in the width direction than both end sections in the axial direction of the inner ring 16.
  • a pair of circular ring shaped washers 22b are provided on the inner diameter side of both end sections in the axial direction (in portions further on the outside in the width direction than both end surfaces in the axial direction of the inner ring 16) of the tappet roller 8c, and between the inside surfaces in the width direction of the support wall sections 12d, 12e and the both end sections in the axial direction of the inner ring 16 with regard to the axial direction of the outer circumferential surface of the support shaft 9b.
  • the outer diameter D 22b of the washers 22b is a little less than the inner diameter d 8 of the tappet roller 8c (D 22b ⁇ d 8 ).
  • the washers 22b are provided in a state so as to cover the opening sections on both ends in the axial direction of the bearing space 21 in which the cylindrical rollers 13 of the radial roller bearing 14 are located.
  • the outer diameter D 22b of the washers 22 is greater than the dimension H 12d in the height direction of the support wall sections 12d, 12e (D 22b > H 12d )
  • FIG. 10 and FIG. 11 illustrate a seventh example of an embodiment of the present invention
  • the inner ring 16b of the fifth example of an embodiment (see FIG. 6 ), and the tappet roller 8c of the sixth example of an embodiment (see FIG. 8 ) are combined to form a radial roller bearing 14d
  • the dimension L 8c in the axial direction of the tappet roller 8c is greater than the dimension L 8 in the axial direction of the tappet roller 8b of the first example of an embodiment (L 8c > L 8 )
  • the dimension L 16b in the axial direction of the inner ring 16b is greater than the dimension L 16 in the axial direction of the inner ring (see FIG.
  • the dimension in the axial direction of the tappet roller and inner ring can be the same as in the first example of an embodiment, and the dimension in the axial direction of the cylindrical rollers can be less than that of the cylindrical rollers 13 of the first example of an embodiment (see FIG. 1 ).
  • a pair of circular ring shaped washers 22c are provided between both end sections in the axial direction of the outer circumferential surface of the inner ring 16b and both end sections in the axial direction of the inner circumferential surface of the tappet roller 8c.
  • the washers 22c are provided in a state so as to cover the opening sections on both ends in the axial direction of the bearing space 21 in which the cylindrical rollers 13 of the radial roller bearing 14d are located
  • the outer diameter D 22c of the washers 22c is greater than the dimension H 12d in the height direction (up-down direction in FIGS 10 and 11 ) of the support wall sections 12d, 12e (D 22c > H 12d ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP12865748.3A 2012-01-19 2012-08-28 Cam follower device Withdrawn EP2806117A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2012008575 2012-01-19
JP2012040874A JP2013167236A (ja) 2012-01-19 2012-02-28 カムフォロア装置
PCT/JP2012/071726 WO2013108433A1 (ja) 2012-01-19 2012-08-28 カムフォロア装置

Publications (1)

Publication Number Publication Date
EP2806117A1 true EP2806117A1 (en) 2014-11-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP12865748.3A Withdrawn EP2806117A1 (en) 2012-01-19 2012-08-28 Cam follower device

Country Status (6)

Country Link
US (1) US20130291817A1 (ja)
EP (1) EP2806117A1 (ja)
JP (1) JP2013167236A (ja)
KR (1) KR20140015562A (ja)
CN (1) CN103635663A (ja)
WO (1) WO2013108433A1 (ja)

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FR3015597B1 (fr) * 2013-12-23 2016-12-23 Skf Ab Dispositif de rouleau suiveur de came
US20150198230A1 (en) * 2014-01-13 2015-07-16 Electro-Motive Diesel Inc. Cam follower assembly having swaged bushing
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KR20140015562A (ko) 2014-02-06
WO2013108433A1 (ja) 2013-07-25

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