WO2015178043A1 - Dispositif suiveur de came - Google Patents

Dispositif suiveur de came Download PDF

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Publication number
WO2015178043A1
WO2015178043A1 PCT/JP2015/050704 JP2015050704W WO2015178043A1 WO 2015178043 A1 WO2015178043 A1 WO 2015178043A1 JP 2015050704 W JP2015050704 W JP 2015050704W WO 2015178043 A1 WO2015178043 A1 WO 2015178043A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
pair
cam follower
plates
follower device
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.)
Ceased
Application number
PCT/JP2015/050704
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English (en)
Japanese (ja)
Inventor
智英 中西
徳如 米田
高井　正樹
篤 内山
勝 井澤
聡 要藤
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.)
Tanaka Seimitsu Kogyo Co Ltd
Original Assignee
Tanaka Seimitsu Kogyo Co 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 Tanaka Seimitsu Kogyo Co Ltd filed Critical Tanaka Seimitsu Kogyo Co Ltd
Publication of WO2015178043A1 publication Critical patent/WO2015178043A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F01L1/18—Rocking arms or levers

Definitions

  • the present invention relates to a cam follower device that constitutes a part of a valve operating device of an internal combustion engine, and more particularly to a cam follower device that rolls into contact with a cam.
  • a system is employed in which a roller is pivotally supported on an installed roller shaft, and this roller is brought into rolling contact with a cam.
  • the cam follower is generally made of an aluminum alloy.
  • the outer ring of the roller and the needle can be in contact with the roller support wall of the cam follower device, when the cam follower device made of aluminum alloy is adopted, the roller having a lower hardness than the roller when the cam follower device is swung by the cam.
  • Patent Document 1 discloses a structure in which washer-like spacers are arranged at both ends of the roller outer ring so as not to contact the roller support wall.
  • Patent Documents 2 and 3 disclose techniques for preventing wear of the roller support wall by providing an engagement portion between the spacer and the roller support wall to prevent the spacer from rotating together.
  • a clearance (see C in FIG. 2B described later) is provided between the roller and the roller support wall to absorb manufacturing errors and guide lubricating oil.
  • the engagement portion see D in FIG. 2B to be described later
  • the engagement portion is in a state where the cam rotates at a high speed.
  • the force generated in the roller is increased, the engaging portion is disengaged, and the roller support wall may eventually be worn.
  • a clearance is provided in the engaging portion between the spacer and the rocker arm to absorb a manufacturing error, and the engaging portion between the spacer and the rocker arm slides within the clearance. Although this sliding does not cause a problem when the rotational speed of the cam is low, there is a possibility that the engaging portion of the rocker arm having low hardness may be worn at a high rotational speed. If this clearance is to be reduced, it is necessary to process the spacer and the rocker arm with high precision, which increases the manufacturing cost.
  • the present invention has been improved in view of the above-described problems, and an object of the present invention is to provide a cam follower device having a structure for improving wear resistance without increasing the manufacturing cost. .
  • the present invention provides a cam follower device having a roller supported by a roller shaft provided between a pair of roller support walls provided at a cam facing portion, and an axial end portion of the roller.
  • a protective plate is formed by connecting one end of a pair of plates provided between surfaces facing the roller support wall by a connecting plate portion, and the pair of plates is pressed against the roller support wall by its elastic force.
  • the distance between the two opposing surfaces of the pair of plates is such that the distance between the other open ends of the pair of plates before assembly is wider than the distance between the opposing roller support walls. It is characterized by gradually increasing from one end to the other end.
  • Engagement comprising a protrusion provided on a pair of plates so as to protrude in the axial direction of the roller to restrict the rotation of the protective plate, and a recess provided on a roller support wall for receiving the protrusion It is preferable to provide a part.
  • a connecting plate portion that connects one end portions of the pair of plates protrudes in a radial direction from the outer ring of the roller to restrict the rotation of the protective plate, and the cam follower device is recessed to receive the protruding portion. It is preferable.
  • the angle formed by two opposing surfaces of the pair of plates is 2 ⁇ , 2 ⁇ is preferably 4 ° to 20 °, and the thickness of the protective plate is preferably 0.1 to 0.5 mm.
  • the height of the protrusion in the roller axial direction is preferably larger than the clearance between the roller and the roller support wall.
  • the material of the protective plate is preferably a spring steel plate, a carbon steel plate or a stainless steel plate.
  • the pair of plates constituting the protection plate are assembled in a state of being pressed against the roller support wall by the elastic force, a frictional force is generated between the pair of plates and the roller support wall for protection.
  • the plate is prevented from co-rotating with the roller. Even if the interval between the opposing roller support walls varies due to manufacturing errors or the like, the pair of plates are assembled in a state of being pressed against the roller support walls by the elastic force, so that the co-rotation is prevented. In this way, it is possible to prevent wear due to contact with the roller support wall while the protective plate rotates.
  • Engagement comprising a protrusion provided on the pair of plates so as to protrude in the axial direction of the roller to restrict the rotation of the protective plate, and a recess provided on the roller support wall for receiving the protrusion
  • a connecting plate portion that connects one end portions of the pair of plates protrudes in a radial direction from the outer ring of the roller to restrict the rotation of the protection plate, and the cam follower device is recessed to receive the protruding portion. Therefore, since the connecting plate portion has a function as the engaging portion, it is possible to further enhance the corotation preventing effect of preventing the protective plate from corotating with the roller. Further, since the connecting plate portion is on the opposite side of the pair of protrusions, when the protective plate is assembled to the cam follower device, the protective plate is simply inserted into the cam follower device in the vertical direction. Each engagement can be easily performed.
  • the angle between the two opposing surfaces of the pair of plates is 2 ⁇
  • 2 ⁇ is 4 ° to 20 °
  • the thickness of the protective plate is 0.1 to 0.5 mm. It can be assembled while being pressed against the roller support wall by force.
  • the height of the projection in the roller axis direction is larger than the clearance between the roller and the roller support wall, preventing the projection from coming out of the recess against the elastic force of the protection plate and preventing the protection plate from co-rotating with the roller. can do.
  • the oil reservoir is provided at the bottom of the depression provided in the roller support wall, lubrication can be performed between the roller and the protective plate and between the roller and the roller support wall, so that the wear resistance can be improved.
  • the material of the protective plate is a spring steel plate, carbon steel plate or stainless steel plate, so that the elastic force of the protective plate can be secured.
  • FIG. 1 is a longitudinal sectional view of a cylinder head portion of an engine.
  • 2A is a cross-sectional view taken along the line 2-2 in FIG. 1
  • FIG. 2B is an enlarged cross-sectional view showing the clearance C between the roller and the roller support wall, and the engagement allowance D of the engaging portion including the protrusion and the depression.
  • FIG. 3 is a cross-sectional view taken along the line 3-3 in FIG.
  • FIG. 4 is a perspective view of the rocker arm.
  • FIG. 5 is a perspective view of the roller.
  • FIG. 6 is another perspective view of the rocker arm.
  • FIG. 7 is a perspective view of the protective plate.
  • FIG. 8 is a side view of the protective plate.
  • FIG. 9A is an enlarged view of an example of a cross section parallel to the connecting plate portion, showing an engaging portion made up of a protrusion and a depression
  • FIG. 9B is a connection showing an engaging portion made up of a protrusion and a depression
  • FIG. 9C is an enlarged view of another example of a cross section parallel to the plate portion
  • FIG. 9C is an enlarged view of still another example of the cross section parallel to the connecting plate portion, showing an engaging portion composed of a protrusion and a depression
  • (D) is an enlarged view of still another example of a cross section parallel to the connecting plate portion, showing an engaging portion composed of a protrusion and a depression.
  • 10A is a cross-sectional view taken along line 10-10 of FIG.
  • FIG. 10B is a diagram showing a modification of FIG. 10A.
  • FIG. 11 is a sectional view taken along line 11-11 of FIG.
  • FIG. 12 is an enlarged view of an example of a cross section parallel to the connecting plate portion, showing an engaging portion composed of a protrusion and a recess having an oil reservoir.
  • 13 is a cross-sectional view taken along line 13-13 of FIG.
  • a cylinder head 2 is coupled to the top surface of a cylinder block 1 of an internal combustion engine, and a piston 4 is slidably fitted to a cylinder 3 provided in the cylinder block 1.
  • Two intake valve holes 2a, 2a and exhaust valve holes 2b, 2b are opened in the combustion chamber 5 formed on the lower surface of the cylinder head 2 so as to face the top surface of the piston 4, and the intake valve holes 2a,
  • An intake port 2c connected to 2a and an exhaust port 2d connected to exhaust valve holes 2b and 2b are formed inside the cylinder head 2.
  • a pair of intake valves (engine valves) 6 and 6 that open and close the intake valve holes 2a and 2a are slidably supported by valve guides 7 and 7 provided in the cylinder head 2, and are closed by intake valve springs 8 and 8, respectively. Be energized by.
  • a pair of exhaust valves 9 and 9 for opening and closing the exhaust valve holes 2b and 2b are slidably supported by valve guides 10 and 10 provided in the cylinder head 2, and attached to the valve closing direction by the exhaust valve springs 11 and 11, respectively. Be forced.
  • FIG. 1 shows only one intake valve 6, valve guide 7, and intake valve spring 8, but in the direction perpendicular to the plane of FIG. 1, another intake valve 6, valve guide 7, and An intake valve spring 8 is provided.
  • 1 shows only one exhaust valve 9, one valve guide 10 and one exhaust valve spring 11. However, another exhaust valve 9 and a valve guide are perpendicular to the plane of FIG. 10 and an exhaust valve spring 11 are provided.
  • the intake camshaft 14 and the exhaust camshaft 15 are rotatably supported between the camshaft holder 12 and the camshaft cap 13 coupled to the top surface of the cylinder head 2.
  • a timing chain 18 is connected to an intake sprocket 16 provided at the shaft end of the intake camshaft 14, an exhaust sprocket 17 provided at the shaft end of the exhaust camshaft 15, and a crank sprocket (not shown) provided at the shaft end of the crankshaft. Is wound, and the intake camshaft 14 and the exhaust camshaft 15 rotate in the same direction at half the number of rotations of the crankshaft.
  • the intake rocker shaft 20 and the exhaust rocker shaft 21 are fixed to the camshaft holder 12.
  • An intake rocker shaft (cam follower device) 22 having adjustment screws 19 and 19 that abut on the stem ends of the intake valves 6 and 6 is swingably supported on the intake rocker shaft 20 positioned below the intake camshaft 14. Yes.
  • adjusting screw 19 is shown in FIG. 1, another adjusting screw 19 is provided in a direction perpendicular to the paper surface of FIG. 1.
  • an exhaust rocker arm 24 having adjustment screws 23 and 23 that are in contact with the stem ends of the exhaust valves 9 and 9 is swingably supported on the exhaust rocker shaft 21 positioned below the exhaust camshaft 15.
  • an adjusting screw 23 is shown in FIG. 1, another adjusting screw 23 is provided in a direction perpendicular to the paper surface of FIG.
  • the material of the intake rocker arm 22 and the exhaust rocker arm 24 is an aluminum alloy for weight reduction, and is manufactured by die casting.
  • the intake cam 25 abuts on a roller 26 provided on the intake rocker arm 22.
  • the following description is given on the intake side, and the same applies to the exhaust side. Therefore, the description on the exhaust side is omitted to avoid redundant description.
  • the intake rocker arm 22 that receives the pressing force of the intake cam 25 via the roller 26 that is in contact with the intake cam 25 causes the intake rocker shaft 20 to move.
  • the pair of intake valves 6, 6 is driven to open and close by swinging to the center and pressing the stem ends of the pair of intake valves 6, 6 with the adjusting screws 19, 19 provided at the tips thereof.
  • the roller since the roller receives the pressing force of the cam while making rolling contact with the cam, the friction loss torque of the valve gear can be reduced.
  • the roller 26 provided on the intake rocker arm 22 shown in FIG. 4 includes an outer ring 28 and a needle 29 that are supported by a roller shaft 27 shown in FIG. At positions where the intake rocker arm 22 faces the intake cam 25 (see FIG. 2 (a)), as shown in FIGS. ing.
  • a roller shaft mounting hole 31 for mounting the roller shaft is formed in the opposing roller support walls 30 and 30, by press-fitting the roller shaft or caulking both end surfaces of the roller shaft.
  • the roller shaft is fixed.
  • the outer ring 28 and the needle 29 are made of an iron-based material having a hardness higher than that of the intake rocker arm 22.
  • a protective plate 32 shown in FIG. 7 is provided between the opposed surfaces of the roller 26 shown in FIG. 4 in the axial direction and the roller support walls 30 and 30. As shown in FIG. 7, the protection plate 32 is connected by a connecting plate 33 at one end opposite to the position facing the cam.
  • the protective plate 32 is an elastic material made of any one of a spring steel plate, a carbon steel plate, and a stainless steel plate, and is preferably subjected to a heat treatment necessary to increase the elastic force. Examples of the material include SUP material, SK material, SUS material, and the like, which can be selected in consideration of the number of rotations of the cam, the magnitude of the force generated in the engaging portion, press workability, and manufacturing cost.
  • the protrusion 35a and the recess 36a have a V-shaped cross section, and any part of the V-shaped cross section of the protrusion 35a and the recess 36a is brought into contact with and engaged with each other.
  • the protection plate 32 since the protection plate 32 is assembled while being pressed against the roller support walls 30 and 30 by its elastic force, the clearance at the engaging portion between the projections 35a and 35b and the recesses 36a and 36b is substantially eliminated. Thus, the protective plate 32 does not slide, and the occurrence of wear at the engaging portion can be prevented.
  • the protective plate 32 can be manufactured at a relatively low cost by pressing, but the protrusions 35a and 35b having a V-shaped cross section can be molded with a lower load than a spherical protrusion. Therefore, the mold is less worn and the projection shape is simple, so that the mold manufacturing cost can be kept low. Further, since the recesses 36a and 36b can be formed only by a simple shape change of the aluminum die-casting mold, it can be manufactured at a low cost.
  • a connecting plate portion 33 that connects one end portions of the protection plate 32 protrudes in a radial direction from the outer ring of the roller 26 in order to restrict the rotation of the protection plate 32, and the rocker arm 22.
  • the connecting plate portion 33 has a function as an engaging portion, so that the protective plate 32 rotates together with the roller 26. The effect of preventing co-rotation can be further enhanced.
  • the V-shaped cross sections do not necessarily need to be in full contact with each other, the height of the protrusion in the roller axial direction or the depth of the recess in the roller axial direction is the tip of the protrusion of the contact portion of both V-shaped cross sections. It refers to the height or depth to the point 37 closest to the side. (See Figure 13)
  • the pair of protrusions 35a and 35b are on the opposite side of the connecting plate portion 33 via the roller axis, and the connecting plate portion 33 is divided equally between the pair of plates 34a and 34b.
  • the pair of protrusions 35a and 35b are in a plane-symmetrical position with respect to a surface (see reference numeral 33a in FIG. 8) that cuts the substrate vertically. Assuming that the projections 35a and 35b and the depressions 36a and 36b are cut in a plane parallel to the connecting plate portion 33, the projection 35a and the depression 36a have a V-shaped cut surface as shown in FIG.
  • the protrusion 35a is pressed against the depression 36a through the V-shaped cut surface by an elastic force.
  • the projection 35b and the depression 36b are not shown, but the projection 35b and the depression 36b also have a V-shaped cut surface like the projection 35a and the depression 36a. It is pressed against the depression 36b side through the V-shaped cut surface.
  • the depth h2 of the V-shaped cut surface in the roller axis direction is gradually shortened from the surface side to the inside, so that the protrusions are pressed against the recesses, The position is also restricted, and wear due to sliding at the engaging portion is less likely to occur.
  • V-shaped cut surface means that when the cut surface is viewed from above, it looks like the shape of the letter “V”, or is close to the shape of the letter “V”, or has the characteristics of the shape of the letter “V”. Say what you have.
  • the characteristic of the shape of the letter “V” can be expressed as “the two sides facing each other through a certain gap at the top gradually narrow the gap and eventually both sides coincide at the bottom”.
  • the protrusion 35a and the recess 36a are in contact with each other with a V-shaped cross section.
  • the character “V” is characterized by “the two sides facing each other through a certain gap at the top. Can be expressed by gradually narrowing the gap and eventually matching both sides at the bottom. "
  • the protrusion 35a and the recess 36a are in full contact with each other with a V-shaped cross section
  • the protrusion 35a-1 and the recess 36a-1 have a V-shaped cross section. It has the part which has touched and the part which has not touched.
  • the projection 35a-1 and the recess 36a-1 are in full contact with the bottom of the V-shape so that the contact area is larger and the wear is less likely to occur.
  • the effect of being difficult to rotate can be obtained in the same manner in both FIG. 9 (a) and FIG. 9 (b).
  • the contact portion between the protrusion and the depression may be a straight portion or a curved portion as shown in FIG. 9A, or only a straight portion as shown in FIG. 9B. From the viewpoint of processing, processing of the linear portion is easier than processing of the curved portion.
  • the structure in which the protrusion and the recess are in contact with each other with a V-shaped cross section is not limited to this, and a structure as shown in FIGS. 9C and 9D can also be adopted.
  • FIG. 9C also shows that the character “V” is shaped according to the above description. “The two sides facing each other through a certain gap at the top gradually narrow the gap, and eventually both sides coincide at the bottom. It can be expressed.
  • the protrusion 35a-2 is in contact with only the corner of the recess 36a-2, but may be in contact with the entire surface.
  • the effect that the projection 35a-2 is in full contact with the recess 36a-2 has a larger contact area and less wear than contact with only the corner, but the protective plate is less likely to rotate with the roller.
  • 35a-2 and depression 36a-2 are in full contact with each other in a V-shaped cross section and when projection 35a-2 is in contact with only the corner of depression 36a-2 as shown in FIG. 9C Either can be obtained in the same way.
  • FIG. 9D is a modification of FIG. 9B.
  • the protrusion 35a-3 and the recess 36a-3 shown in FIG. 9D are straight at the portion in contact with the V-shaped cross section, and further have flat portions f1 and f2.
  • the length L1 of the flat part f1 is longer than or the same as the length L2 of the flat part f2.
  • the contact area is larger and wears less when L1 and L2 are the same length, but the effect that the protective plate is difficult to rotate with the roller is that L1 is longer than L2. It can be obtained in the same way whether L1 and L2 are equal in length.
  • the depth h2 of the V-shaped cut surface in the roller axis direction is gradually shortened from the surface side to the inside, and the V-shaped cross sections are in full contact with each other.
  • a part of the V-shaped cross section may be in contact.
  • the structure of FIG. 10A in which the V-shaped cross-sections are in full contact with each other has a larger contact area than the structure of FIG. 10B in which a part of the V-shaped cross-section is in contact.
  • the height h1 in the roller axial direction of the protrusion 35a is equal to or higher than the depth h2 in the roller axial direction of the recess 36a so that any one of the recesses 36a and 36b is brought into contact with and engaged with each other. Since it is set (because the height h1 of the protrusion 35b in the roller axial direction is set to be the same as or higher than the depth h2 of the recess 36b in the roller axial direction), the protective plate 32 slides. There is no.
  • the present invention can be suitably used for a cam follower device that constitutes a part of a valve operating device of an internal combustion engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

La présente invention concerne un dispositif suiveur de came possédant une structure qui augmente les propriétés de résistance à l'usure sans augmenter le coût de fabrication. Un dispositif suiveur de came est pourvu d'une plaque de protection formée par le raccordement d'une extrémité de chaque plaque d'une paire de plaques l'une à l'autre par une section plaque de raccordement, les plaques étant chacune situées entre les surfaces se faisant face de chacune des extrémités axiales d'un rouleau (26) et une paroi (30) de support de rouleau correspondante. La distance entre deux surfaces se faisant face de la paire de plaques augmente progressivement depuis lesdites extrémités de la paire de plaques jusqu'à ses autres extrémités qui sont ouvertes, rendant la distance entre les autres extrémités avant que la paire de plaques ne soit montée plus grande que la distance entre les parois (30) de support de rouleau qui se font mutuellement face et, par conséquent, la paire de plaques est montée tout en étant pressée contre les parois (30) de support de rouleau par la force élastique de la paire de plaques.
PCT/JP2015/050704 2014-05-19 2015-01-14 Dispositif suiveur de came Ceased WO2015178043A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-103591 2014-05-19
JP2014103591A JP5627158B1 (ja) 2014-05-19 2014-05-19 カムフォロア装置

Publications (1)

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WO2015178043A1 true WO2015178043A1 (fr) 2015-11-26

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PCT/JP2015/050704 Ceased WO2015178043A1 (fr) 2014-05-19 2015-01-14 Dispositif suiveur de came

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WO (1) WO2015178043A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107313822A (zh) * 2017-06-29 2017-11-03 绵阳富临精工机械股份有限公司 一种带有储油槽的摇臂
CN109514003A (zh) * 2018-09-30 2019-03-26 宁波爱柯迪精密部件有限公司 铝压铸件加工设备和加工方法及铝压铸件

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7140696B2 (ja) 2019-02-22 2022-09-21 株式会社オティックス ロッカアーム

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6229405U (fr) * 1985-08-08 1987-02-23
JPS648510U (fr) * 1987-07-06 1989-01-18
JPS6429204U (fr) * 1987-08-17 1989-02-21
JPS6432405U (fr) * 1987-08-21 1989-03-01
JPH0280703U (fr) * 1988-12-13 1990-06-21
JP2003013711A (ja) * 2001-07-02 2003-01-15 Honda Motor Co Ltd ロッカアーム
JP2003112225A (ja) * 2001-10-04 2003-04-15 Nsk Ltd ロッカーアーム
JP2010168941A (ja) * 2009-01-21 2010-08-05 Nsk Ltd カムフォロア装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6229405U (fr) * 1985-08-08 1987-02-23
JPS648510U (fr) * 1987-07-06 1989-01-18
JPS6429204U (fr) * 1987-08-17 1989-02-21
JPS6432405U (fr) * 1987-08-21 1989-03-01
JPH0280703U (fr) * 1988-12-13 1990-06-21
JP2003013711A (ja) * 2001-07-02 2003-01-15 Honda Motor Co Ltd ロッカアーム
JP2003112225A (ja) * 2001-10-04 2003-04-15 Nsk Ltd ロッカーアーム
JP2010168941A (ja) * 2009-01-21 2010-08-05 Nsk Ltd カムフォロア装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107313822A (zh) * 2017-06-29 2017-11-03 绵阳富临精工机械股份有限公司 一种带有储油槽的摇臂
CN109514003A (zh) * 2018-09-30 2019-03-26 宁波爱柯迪精密部件有限公司 铝压铸件加工设备和加工方法及铝压铸件

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JP2015218668A (ja) 2015-12-07

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