US20120304957A1 - Bearing oil feed device - Google Patents

Bearing oil feed device Download PDF

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Publication number
US20120304957A1
US20120304957A1 US13/579,342 US201013579342A US2012304957A1 US 20120304957 A1 US20120304957 A1 US 20120304957A1 US 201013579342 A US201013579342 A US 201013579342A US 2012304957 A1 US2012304957 A1 US 2012304957A1
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United States
Prior art keywords
bearing
connecting rod
lubricating oil
main
upper side
Prior art date
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Abandoned
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US13/579,342
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English (en)
Inventor
Kenji Watanabe
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Taiho Kogyo Co Ltd
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Taiho Kogyo Co Ltd
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Assigned to TAIHO KOGYO CO., LTD. reassignment TAIHO KOGYO CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WATANABE, KENJI
Publication of US20120304957A1 publication Critical patent/US20120304957A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/14—Features relating to lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/022—Sliding-contact bearings for exclusively rotary movement for radial load only with a pair of essentially semicircular bearing sleeves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
    • F16C17/246—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety related to wear, e.g. sensors for measuring wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • F16C33/1055—Details of supply of the liquid to the bearing from radial inside, e.g. via a passage through the shaft and/or inner sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/046—Brasses; Bushes; Linings divided or split, e.g. half-bearings or rolled sleeves

Definitions

  • the present invention relates to a bearing oil feed device, and more particularly to a bearing oil feed device which is favorable in a case of feeding oil to a crankshaft of an engine for an automobile, for example.
  • an engine for an automobile for example, includes a crankshaft including a plurality of main shafts and crank pins, a plurality of main bearings each configured by a semi-cylindrical upper side bearing member and lower side bearing member which pivotally and rotatably and supports the above described main shaft at a cylinder block, and a plurality of connecting rod bearings which pivotally and rotatably support the above described crankpins at connecting rods.
  • the bearing oil feed device in which an oil groove is formed in an entire periphery of the upper side bearing member of the main bearing, the oil groove is opened to a joint portion of a half-split bearing and a space is formed in the joint portion, whereby a foreign substance in the oil groove is discharged from the main bearing with the lubricating oil to make it difficult for the above described foreign substance from entering the connecting rod bearing via the internal passage formed in the crankshaft ( FIG. 2 of Patent Literature 4).
  • Patent Literature 1 Japanese Patent Laid-Open No. 4-219521
  • Patent Literature 2 Japanese Patent Laid-Open No. 5-215125
  • Patent Literature 3 Japanese Patent Laid-Open No. 7-27127
  • Patent Literature 4 Japanese Patent Laid-Open No. 2005-076755
  • the present invention provides a bearing oil feed device which suppresses an amount of a lubricating oil which is discharged from a sliding portion of a main bearing, and can prevent damage to the main bearing and a connecting rod bearing due to a foreign substance which flow in the above described lubricating oil as much as possible.
  • a bearing oil feed device is a bearing oil feed device including a crankshaft including a plurality of main shafts and crankpins, a plurality of main bearings which are each configured by a semi-cylindrical upper side bearing member and lower side bearing member, and each pivotally supports the main shaft rotatably at a cylinder block, and a plurality of connecting rod bearings which each pivotally supports the crankpin rotatably at a connecting rod,
  • a radial hole which communicates with a lubricating oil passage formed inside the cylinder block is formed in the upper side bearing member in the main bearing, and a lubricating oil which is supplied to a sliding portion of the main bearing and the main shaft via the radial hole is supplied to a sliding portion of the crankpin and the connecting rod bearing via an internal passage which is formed inside the crankshaft and is opened to the main shaft and the crankpin,
  • a space D between an end portion of the partial groove and each of crush reliefs formed at both ends in a circumferential direction of the upper side bearing member is provided within a range of
  • a depth gradually decreasing portion which is formed to be arc-shaped in section seen from an axial direction of the upper side bearing member is formed at the end portion of the partial groove, and a radius r of the depth gradually decreasing portion is provided within a range of
  • a lubricating oil discharge passage which communicates with the internal passage formed in the crankshaft to discharge the lubricating oil is provided in the connecting rod bearing.
  • a bearing oil feed device is a bearing oil feed device including a crankshaft including a plurality of main shafts and crankpins, a plurality of main bearings which each pivotally supports the main shaft rotatably at a cylinder block, and are each configured by a semi-cylindrical upper side bearing member and lower side bearing member, and a plurality of connecting rod bearings which each pivotally supports the crankpin rotatably at a connecting rod,
  • a radial hole which communicates with a lubricating oil passage formed inside the cylinder block is formed in the upper side bearing member in the main bearing, and a lubricating oil which is supplied to a sliding portion of the main bearing and the main shaft via the radial hole is supplied to a sliding portion of the crankpin and the connecting rod bearing via an internal passage which is formed inside the crankshaft and is opened to the main shaft and the crankpin,
  • a space D between an end portion of the partial groove and each of crush reliefs formed at both ends in a circumferential direction of the upper side bearing member is provided within a range of
  • a depth gradually decreasing portion with a depth gradually decreasing is formed at the end portion of the partial groove, and an angle ⁇ formed by the depth gradually decreasing portion and the inner circumferential surface of the upper side bearing member is provided within a range of
  • a lubricating oil discharge passage which communicates with the internal passage formed in the crankshaft to discharge the lubricating oil is provided in the connecting rod bearing.
  • the depth gradually decreasing portion of the inner groove formed in the upper side bearing member of the above described main bearing is formed in conformity with the above described conditions, whereby the lubricating oil is stopped by the above described depth gradually decreasing portion, and the discharge amount of the lubricating oil from the sliding portion of the main shaft and the main bearing can be suppressed.
  • the foreign substance in the lubricating oil can be also kept to stay in the above described depth gradually decreasing portion, and when the internal passage formed in the crankshaft communicates with the depth gradually decreasing portion, the foreign substance can be caused to flow into the internal passage together with the above described lubricating oil.
  • the foreign substance is discharged from the lubricating oil discharge passage formed in the above described connecting rod bearing, and therefore, damage to the above described main bearing and the connecting rod bearing due to the foreign substance is prevented.
  • FIG. 1 is a sectional view of a main part showing a first embodiment of the present invention.
  • FIG. 2 is a partial enlarged view of a main bearing.
  • FIG. 3 is a partial enlarged view of a connecting rod bearing.
  • FIG. 4 is a graph showing an experimental result.
  • FIG. 5 is a graph showing an experimental result.
  • FIG. 6 is a partial enlarged view of a main bearing in a second embodiment.
  • FIG. 7 is a partial enlarged view of a connecting rod bearing in the second embodiment.
  • FIG. 8 is a graph showing an experimental result.
  • FIG. 1 shows a sectional view of a main part of an engine 1 for an automobile as a bearing oil feed device, and the engine 1 includes a cylinder block 2 , a crankshaft 3 pivotally supported rotatably at the cylinder block 2 , and a connecting rod 4 pivotally supported rotatably at the crankshaft 3 .
  • crankshaft 3 is configured by a main shaft 3 A pivotally supported at the cylinder block 2 via a main bearing 5 , a crankpin 3 B pivotally supported at the connecting rod 4 via a connecting rod bearing 6 , and a connecting member not illustrated which connects the main shaft 3 A and the crankpin 3 B.
  • An internal passage 3 C which allows the lubricating oil to flow therethrough is formed inside the crankshaft 3 , and the internal passage 3 C opens at a position opposed to a diameter direction of an outer circumferential surface in the main shaft 3 A, and is formed in an oblique direction from one opening in the main shaft 3 A to open to an outer circumferential surface of the crankpin 3 B.
  • the above described main bearing 5 is configured to be cylindrical by butting a semi-cylindrical upper side bearing member 11 and a semi-cylindrical lower side bearing member 12 which are a pair of upper and lower members, and the main bearing 5 is fixed to the above described cylinder block 2 by a cap 13 an inner surface of which is formed into a semicircular shape.
  • the main shaft 3 A of the above described crankshaft 3 slides in contact with inner circumferential surfaces of the upper side bearing member 11 and the lower side bearing member 12 , and the inner circumferential surface of the main bearing 5 and the outer circumferential surface of the main shaft 3 A configure a sliding portion.
  • a lubricating oil passage 2 A is formed inside the above described cylinder block 2 , a radial hole 11 a is formed in the upper side bearing member 11 of the main bearing 5 to correspond to a position of a lower end portion of the lubricating oil passage 2 A.
  • the lubricating oil which flows via the above described lubricating oil passage 2 A is supplied to the sliding portion of the main bearing 5 and the main shaft 3 A via the radial hole 11 a, and lubricates the sliding portion.
  • the main bearing 5 of the present embodiment is provided with a partial groove 14 which is formed in a circumferential direction in the inner circumferential surface of the above described upper side bearing member 11 , and the partial groove 14 communicates with the opening of the internal passage 3 C of the main shaft 3 A which rotates.
  • FIG. 2 shows an enlarged view of a border portion of the upper side bearing member 11 and the lower side bearing member 12 in the above described main bearing 5 , and in a joint portion of both the bearing members 11 and 12 , crush reliefs 11 b and 12 a and chamfers 11 c and 12 b are formed respectively.
  • the above described partial groove 14 is configured by a groove portion 14 a which is formed with a predetermined depth, and a depth gradually decreasing portion 14 b which is adjacent to the groove portion 14 a and has the depth gradually decreasing up to a position the inner circumferential surface, and the above described radial hole 11 a opens to the above described groove portion 14 a.
  • An end portion of the above described partial groove 14 that is, a position at which a depth of the depth gradually decreasing portion 14 b becomes zero is set within the following range when a distance between the end portion of the partial groove 14 and the above described crush relief 11 b is set as D.
  • the above described depth gradually decreasing portion 14 b is machined to be in a circular arc shape of a radius r when seen from the axial direction of the main bearing 5 , and the radius r of the depth gradually decreasing portion 14 b is set within the following range.
  • the connecting rod bearing 6 is configured to be cylindrical by butting a pair of upper and lower half-split bearings 21 and 22 , and is held by semicircular recessed portions formed in a connecting rod main body 4 a and a connecting rod cap 4 b.
  • crankpin 3 B of the above described crankshaft 3 is in sliding contact with inner circumferential surfaces of the two half-split bearings 21 and 22 , and the inner circumferential surface of the connecting rod bearing 6 and the outer circumferential surface of the crankpin 3 B configure a sliding portion.
  • FIG. 3 shows a partial enlarged view of the connecting rod bearing 6 , in a joint portion of the half-split bearings 21 and 22 , crush reliefs 21 a and 22 a and chamfers 21 b and 22 b are formed respectively, and the joint portion is provided with a lubricating oil discharge passage 23 which communicates with the internal passage 3 c formed in the crankshaft 3 to discharge the lubricating oil.
  • the above described lubricating oil discharge passage 23 is configured by a through-hole 23 a which is formed in a position of the above described joint portion and penetrates in a radial direction, and a foreign substance discharge groove 23 b which is formed in outer circumferential surfaces of the half-split bearings 21 and 22 and communicates with the above described through-hole 23 a.
  • the above described through-hole 23 a is provided by being bored in a central portion in the axial direction in the connecting rod bearing 6 , and is formed in a position superimposed on a movement trajectory of the opening of the internal passage 3 C by rotation of the crankpin 3 B.
  • an inside diameter of the through-hole 23 a is set to be a dimension which allows the maximum foreign substance assumed to be included in the lubricating oil to pass, and is set to be larger than an inside diameter of the internal passage 3 C which opens to the above described crankpin 3 B.
  • the above described foreign substance discharge groove 23 b is configured by two notches formed respectively at edge portions of the outer circumferential surfaces of the above described two half-split bearings 21 and 22 , and are respectively formed to penetrate in the axial direction of the connecting rod bearing 6 .
  • a width of the foreign substance discharge groove 23 b is set to be a dimension smaller than the inside diameter of the above described through-hole 23 a, and a depth of the foreign substance discharge groove 23 b is set at such a dimension as to allow a foreign substance of the maximum size which is assumed in advance to pass.
  • a space is formed between the above described foreign substance discharge groove 23 b and the inner circumferential surface of the connecting rod 4 , and the lubricating oil which passes through the above described through-hole 23 a is discharged from end surfaces at both sides of the connecting rod 4 via the space.
  • the lubricating oil passes through the lubricating oil passage 2 A of the cylinder block 2 , and thereafter, is supplied into the partial groove 14 of the main bearing 5 via the radial hole 11 a formed in the upper side bearing member 11 of the main bearing 5 .
  • a part of the lubricating oil lubricates the sliding portion of the main bearing 5 and the main shaft 3 A from the partial groove 14 , whereas the other lubricant oil moves along the circumferential direction of the upper side bearing member 11 inside the above described partial groove 14 with rotation of the main shaft 3 A, and thereafter, moves to the depth gradually decreasing portion 14 b of the partial groove 14 .
  • the above described depth gradually decreasing portion 14 b is formed to be abruptly shallow based on the above described (expression 2 ), and therefore, the lubricating oil in the partial groove 14 is stopped by the depth gradually decreasing portion 14 b.
  • the depth gradually decreasing portion 14 b is formed in a position separated from the crush relief lib based on the above described (expression 1), and therefore, the blocked lubricating oil is prevented from moving to the crush relief 11 b via a gap between the inner circumferential surface of the upper side bearing member 11 and the outer circumferential surface of the main shaft 3 A.
  • the lubricating oil is stopped by the above described depth gradually decreasing portion 14 b, whereby the amount of the lubricating oil which is discharged outside from the sliding portion of the main shaft 3 A and the main bearing 5 can be suppressed, and the sliding portion of the main shaft 3 A and the main bearing 5 is lubricated by a suitable amount of the lubricating oil.
  • the foreign substance in the partial groove 14 moves to the depth gradually decreasing portion 14 b of the partial groove 14 with the lubricating oil, but the foreign substance is inhibited from moving outside the partial groove 14 by the depth gradually decreasing portion 14 b similarly to the lubricating oil.
  • the foreign substance staying in the depth gradually decreasing portion 14 b flows into the internal passage 3 C simultaneously with the above described lubricating oil flowing into the internal passage 3 C at once when the internal passage 3 C which opens to the above described main shaft 3 A passes the depth gradually decreasing portion 14 b.
  • the foreign substance in the lubricating oil which flows in the above described partial groove 14 flows into the internal passage 3 C of the crankshaft 3 without entering between the main shaft 3 A and the main bearing 5 , owing to the depth gradually decreasing portion 14 b, and therefore, damage of the sliding portion of the main shaft 3 A and the main bearing 5 due to foreign substance is prevented.
  • the lubricating oil which flows into the internal passage 3 C moves to the crankpin 3 B side with the rotation of the crankshaft 3 , and thereafter, is discharged to the sliding portion with the connecting rod bearing 6 from the opening which is formed in the outer periphery of the crankpin 3 B.
  • a part of the lubricating oil lubricates the sliding portion of the crankpin 3 B and the connecting rod bearing 6 , and the other lubricating oil is discharged outside the connecting rod 4 from the lubricating oil discharge passage 23 formed in the above described connecting rod bearing 6 .
  • the opening of the internal passage 3 C formed in the above described crankpin 3 B reaches the joint portion of the two half-split bearings 21 and 22 , the opening of the internal passage 3 C communicates with the through-hole 23 a of the above described lubricating oil discharge passage 23 , and the lubricating oil in the internal passage 3 C flows into the above described foreign substance discharge groove 23 b via the through-hole 23 a.
  • the foreign substance discharge groove 23 b is formed in the axial direction of the connecting rod bearing 6 , and therefore, the lubricating oil is discharged outside the connecting rod 4 from the end surfaces at both sides of the connecting rod bearing 6 via the foreign substance discharge groove 23 b.
  • the foreign substance contained in the lubricating oil in the above described internal passage 3 C is also discharged outside the connecting rod 4 from the lubricating oil discharge passage 23 , whereby damage to the crankpin 3 B and the connecting rod bearing 6 due to the foreign substance is prevented, and the through-hole 23 a and the foreign substance discharge groove 23 b are formed to be larger than the foreign substance, whereby the foreign substance does not close the lubricating oil discharge passage 23 .
  • the partial groove 14 is formed in the upper side bearing member 11 of the main shaft 3 A, and the depth gradually decreasing portion 14 b of the partial groove 14 is formed under the conditions of the above described (expression 1) and (expression 2), whereby most of the lubricating oil which is supplied to the sliding portion of the main shaft 3 A and the main bearing 5 can be caused to flow into the internal passage 3 C which is formed in the crankshaft 3 .
  • the amount of the lubricating oil which is discharged from the sliding portion of the main shaft 3 A and the main bearing 5 can be suppressed, and the foreign substance contained in the lubricating oil can be discharged to the internal passage 3 C, whereby damage to the main shaft 3 A and the main bearing 5 can be prevented.
  • the foreign substance contained in the lubricating oil which is supplied to the above described internal passage 3 C is discharged outside the connecting rod 4 together with the lubricating oil by the lubricating oil discharge passage 23 which is formed in the above described connecting rod bearing 6 , and therefore, damage to the crankpin 3 B and the connecting rod bearing 6 by the foreign substance can be also prevented.
  • FIG. 4 and FIG. 5 show graphs showing experimental results of the engine 1 according to the above described embodiment.
  • the above described engine 1 was operated in a state in which the internal passage 3 C of the crankshaft 3 having the above described configuration was closed, and a predetermined amount of foreign substance was mixed into the lubricating oil which was supplied from the lubricating oil passage 2 A of the above described cylinder block 2 , and how much foreign substance remained in the partial groove 14 formed in the upper side bearing member 11 in the above described main shaft 3 A was measured.
  • FIG. 4 is the experimental result about expression 1, and an axis of abscissa represents a distance D between the end portion of the partial groove 14 and the crush relief 11 b , whereas an axis of ordinates represents a ratio of the foreign substance mixed via the lubricating oil passage 2 A being recovered by the above described partial groove 14 .
  • an radius r of the depth gradually decreasing portion 14 b in expression 2 is set as a radius of the inner circumferential surface of the main shaft 3 A ⁇ 0.5.
  • FIG. 5 is an experimental result about expression 2 , and the axis of abscissa represents a radius r of the depth gradually decreasing portion 14 b, whereas the axis of ordinates represents a ratio of the foreign substance mixed via the lubricating oil passage 2 A being recovered by the above described partial groove 14 .
  • the distance D between the end portion of the partial groove 14 and the crush relief 11 b in expression 1 is set at 2 mm.
  • FIG. 6 and FIG. 7 show partial sections of the engine 1 of a second embodiment according to the present invention
  • FIG. 6 shows an partial enlarged view of the main bearing 5 similarly to FIG. 2 of the above described first embodiment
  • FIG. 7 shows a partial enlarged view of the connecting rod bearing 6 similarly to FIG. 3 of the above described first embodiment.
  • the partial groove 14 is formed in the upper side bearing member 11 of the main shaft 3 A in the second embodiment, and to the distance D between the end portion of the partial groove 14 and the crush relief 11 b, the relation of (expression 1) in the above described first embodiment is applied.
  • an angle ⁇ which is formed by the depth gradually decreasing portion 14 b and the inner circumferential surface of the upper side bearing member 11 is set within the following range.
  • a lubricating oil discharge passage 123 is formed in the inner circumferential surface of the connecting rod bearing 6 , is more specifically configured by crush reliefs 21 a and 22 a which are formed in a connection portion of the above described half-split bearings 21 and 22 , and chamfers 21 b and 22 b which are formed adjacently to the crush reliefs 21 a and 22 a, and a foreign substance discharge groove 123 a is formed by the crush reliefs 21 a and 22 a and the chamfers 21 b and 22 b.
  • a depth from the outer circumferential surface of the above described crankpin 3 B to bottom portions of the chamfers 21 b and 22 b in the above described foreign substance discharge groove 123 a is set at a dimension which enables a maximum foreign substance assumed to be mixed in the lubricating oil to pass.
  • a space by the above described foreign matter discharge groove 123 a is formed between the outer circumferential surface of the above described crankpin 3 B and the inner circumferential surface of the connecting rod bearing 6 , and the space is penetrated in the axial direction of the connecting rod bearing 6 to communicate with an outside of the connecting rod 4 .
  • the lubricating oil flows through the lubricating oil passage 2 A of the cylinder block 2 , after which, the lubricating oil is discharged to the sliding portion of the main bearing 5 and the main shaft 3 A via the radial hole 11 a formed in the upper side bearing member 11 of the main bearing 5 , and the lubricating oil is supplied into the partial groove 14 which is formed in the upper side bearing member 11 .
  • the lubricating oil in the partial groove 14 is stopped by the depth gradually decreasing portion 14 b because the depth gradually decreasing portion 14 b is formed in such a manner that the depth of the partial groove 14 abruptly becomes small based on the above described (expression 3).
  • the depth gradually decreasing portion 14 b is formed at the position separated from the crush relief 11 b based on the above described (expression 1), and therefore, the lubricating oil which is stopped does not move to the crush relief 11 b via a gap between the inner circumferential surface of the upper side bearing member 11 and the main shaft 3 A.
  • the foreign substance in the lubricating oil also remains in the partial groove 14 by the depth gradually decreasing portion 14 b, and when the opening of the internal passage 3 C which is formed in the main shaft 3 A is located at the depth gradually decreasing portion 14 b thereafter, the foreign substance flows into the internal passage 3 C together with the lubricating oil.
  • the partial groove 14 is formed in the upper side bearing member 11 of the main shaft 3 A, and the depth gradually decreasing portion 14 b of the partial groove 14 is formed under the conditions of the above described (expression 1) and (expression 3), whereby most of the lubricating oil which is supplied to the sliding portion of the main shaft 3 A and the main bearing 5 can be caused to pass into the internal passage 3 C which is formed in the crankshaft 3 .
  • the amount of the lubricating oil which is discharged from the sliding portion of the main shaft 3 A and the main bearing 5 can be suppressed, and because the foreign substance contained in the lubricating oil can be discharged to the internal passage 3 C, damage to the main shaft 3 A and the main bearing 5 can be prevented.
  • the foreign substance contained in the lubricating oil which is supplied to the above described internal passage 3 C is discharged outside the connecting rod 4 together with the lubricating oil by the lubricating oil discharge passage 123 which is formed in the above described connecting rod bearing 6 , and therefore, damage to the crankpin 3 B and the connecting rod bearing 6 due to the foreign substance can be also prevented.
  • FIG. 8 shows a graph showing an experimental result about the engine 1 according to the above described second embodiment.
  • the experiment was performed by operating the engine 1 with the internal passage 3 C of the above described crankshaft 3 being closed, and mixing a predetermined amount of foreign substance into the lubricating oil which was supplied from the lubricating oil passage 2 A of the above described cylinder block 2 .
  • FIG. 8 is the experimental result about expression 3 , and the axis of abscissa represents the angle ⁇ formed by the depth gradually decreasing portion 14 b and the inner circumferential surface of the upper side bearing member 11 , whereas the axis of ordinates represents the ratio of the foreign substance mixed via the lubricating oil passage 2 A being recovered by the above described partial groove 14 .
  • the distance D between the end portion of the partial groove 14 and the crush relief 11 b in expression 1 is set as 2 mm.
  • the range of expression 3 is further desirably set as the range of 30 ⁇ 45°.
  • the connecting rod bearing 6 according to the above described second embodiment may be used, and in the engine 1 in the second embodiment, the connecting rod bearing 6 according to the above described first embodiment may be used.
  • so-called jet holes which are formed to penetrate through the outer surface of the connecting rod 4 from the inner circumferential surface of the connecting rod bearing 6 may be adopted in place of the lubricating oil discharge passages 23 and 123 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Ocean & Marine Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
US13/579,342 2010-02-26 2010-11-05 Bearing oil feed device Abandoned US20120304957A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2010-043450 2010-02-26
JP2010043450A JP5645001B2 (ja) 2010-02-26 2010-02-26 軸受給油装置
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US20130167792A1 (en) * 2012-01-04 2013-07-04 Schaeffler Technologies AG & Co. KG Self-lubricating balance shaft with flow control
US20140064644A1 (en) * 2012-08-31 2014-03-06 Daido Metal Company Ltd. Connecting rod bearing
US9500225B2 (en) 2012-08-01 2016-11-22 Taiho Kogyo Co., Ltd. Sliding bearing
CN109057962A (zh) * 2018-08-16 2018-12-21 重庆卓力标准件制造有限公司 一种摩托车曲轴连杆总成

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JP2015001250A (ja) 2013-06-14 2015-01-05 大同メタル工業株式会社 軸受装置
JP2015001251A (ja) * 2013-06-14 2015-01-05 大同メタル工業株式会社 軸受装置
CN104728270B (zh) * 2015-03-28 2017-06-27 哈尔滨广瀚动力传动有限公司 一种用于两级行星齿轮装置连接筒的阻尼轴承
CN110520640B (zh) * 2017-03-24 2022-01-14 江森自控科技公司 压力坝轴承

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CN109057962A (zh) * 2018-08-16 2018-12-21 重庆卓力标准件制造有限公司 一种摩托车曲轴连杆总成

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CN102782345A (zh) 2012-11-14
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JP5645001B2 (ja) 2014-12-24
WO2011104940A1 (ja) 2011-09-01
EP2541080A1 (de) 2013-01-02
JP2011179572A (ja) 2011-09-15

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