GB1582075A - Arrangement for lubricating a crankpin bearing - Google Patents

Arrangement for lubricating a crankpin bearing Download PDF

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Publication number
GB1582075A
GB1582075A GB4145877A GB4145877A GB1582075A GB 1582075 A GB1582075 A GB 1582075A GB 4145877 A GB4145877 A GB 4145877A GB 4145877 A GB4145877 A GB 4145877A GB 1582075 A GB1582075 A GB 1582075A
Authority
GB
United Kingdom
Prior art keywords
oil
angle
lubricating
crankpin
bores
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.)
Expired
Application number
GB4145877A
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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 Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Publication of GB1582075A publication Critical patent/GB1582075A/en
Expired legal-status Critical Current

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Classifications

    • 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
    • F16C37/00—Cooling of bearings
    • F16C37/002—Cooling of bearings of fluid bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • 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
    • 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
    • F16C9/04—Connecting-rod bearings; Attachments thereof

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Description

(54) AN ARRANGEMENT FOR LUBRICATING A CRANKPIN BEARING (71) We ,KLOCKNER-HUMBOLDT- DEUTZ AKTIENGESELLSCHAFT, a German Body Corporate, of Koln-Deutz, German Federal Republic, do hereby declare the invention for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: This invention relates to a reciprocatingpiston internal combustion engine comprising an arrangement for lubricating a big-end bearing and cooling the associated piston.
It is already known for the associated crankpin of such an arrangement to be supplied with lubricating oil via bores in the crankshaft and the crankpin, the oil being conveyed to the piston via a part-peripheral groove in the big-end bearing shell extending over a limited angular region and subtending an angle ss of less than 180 at the crankpin axis. The part-peripheral groove is connected to a lubricating-oil bore in the associated connecting rod, while the crankpin is provided with two radial lubricatingoil bores which subtend an angle a of less than 1800 at the crankpin axis and are so disposed with respect to the part-peripheral groove that the flow of oil to the connecting rod is interrupted in a selectable angular region which is symmetrical with respect to the lower dead-centre point.
The purpose of the above-described arrangement is to increase the oil flow through the big-end bearing and the connecting rod so as to prevent oil from flowing back into the lubricating-oil bore in the connecting rod as a result of the inertia of the oil column. In this known system, the sum of the angles a and ss is between 142 and 162". In many cases, however, (and particularly in Diesel engines,) this range is insufficient to provide an optimum oil supply.
In another known system for lubricating a big-end bearing, the crankpin has only one lubricating bore. This bore co-operates with a groove extending over an angular distance of 240". A disadvantage of this sytem however is that the load capacity is greatly reduced by the groove over a relatively large peripheral region of the big-end bearing.
Even if the groove is formed in the lower half of the bearing shell, which is not subjected to the combustion gas, the bearing may be damaged by the forces of inertia which increase with the speed of rotation.
It is accordingly an aim of the present invention to ensure an optimum flow of oil with a minimum reduction of the load capacity of the bearing by peripheral lubricating-oil grooves. To this end, the invention is directed to a reciprocating-piston internal comprising means for lubricating a big-end bearing and cooling the associated pistion, in which: (a) the associated crankpin is supplied with lubricating oil via bores in the crankshaft and crankpin; (b) the oil is conveyed to the piston via a part-peripheral groove in the big-end bearing shell extending over a limited angular region and subtending an angle ss of less than 1800 at the crankpin axis, the partperipheral groove being connected to a lubricating-oil bore in the associated connecting rod; and (c) at least two radial, angularly-spaced, lubricating-oil bores are provided in the crankpin with the angle a between the two bores, or between the two outer bores where more than two are provided, being less than 1800 at the crankpin axis, the said bores in the crankpin defining an angle of relative rotation between the crankpin and the big-end bearing shell within which the said bores communicate with the partperipheral groove and being so disposed with respect to the part-peripheral groove that the flow of oil is interrupted in a selectable angular region which is symmetrical with respect to the lower dead-centre point; the sum of the angles a and p being between 280 and 1900 for average piston speeds between 8 and 10 metres per second and between 240 and 1800 for average piston speeds above 10 metres per second.
The present invention is based on the discovery that the average piston speed is related to the optimum oil flow rate; at low piston speeds, a larger peripheral groove is advantageous since it increases the flow rate of oil and, as a result of the lower inertia, a part of the bearing is more lightly stressed, so that a larger groove may be used without disadvantage. At higher piston speeds the optimum oil flow rate is displaced towards lower angular regions, but the region of reduced load capacity is simultaneously reduced by the smaller groove. In addition, the oil flow rate is dependent on the oil pressure, so that the upper tolerance region can be set at a higher lubricating-oil pressure of approximately 7 atmospheres gauge and the lower tolerance region can be set at lubricating-oil pressures of approximately 3 atmospheres gauge.
According to a preferred feature of the invention, in order to reduce the region of the bearing shell which is adversely affected by the groove the angle a is greater than the angle P between the two ends of the part-peripheral groove. For this purpose, three radial grooves are provided in the crankpin, with the angle a being subtended by the two outer bores and the third radial lubricating-oil bore dividing the angle a so that both the partial angles are smaller than the angle ss. As an alternative solution, the angle a between the two radial lubricating oil bores is greater than the angle ss between the two ends of the part-peripheral groove, and the crankpin comprises part-peripheral lubricating-oil grooves leading from the radial lubricating-oil bores and directed towards one another, the length of the grooves being such that the angle a sub tended by their ends is equal to or less than the angle ss.
Two examples of arrangements in accord ance with the invention are shown in the accompanying drawings, in which: - Figure 1 is a cross-section through an arrangement according to the invention for lubricating a big-end bearing, comprising three radial lubricating-oil bores in the crankpin; and Figure 2 is a cross-section through an arrangement according to the invention for lubricating a big-end bearing having two radial lubricating-oil bores in the crankpin, and groove extensions.
A main shaft part 1 of a crankshaft 2 has lubricating-oil bores 3 and 4 through which lubricating oil is supplied to a crankpin 5.
Crankpin 5 has radial lubricating-oil bores 6 and 7 whose axes subtend an angle a at the crankpin axis, which angle, in the example shown, is approximately 1300. An additional radial lubricating-oil bore 12 is disposed between bores 6 and 7 and bisects the angle a.
A connecting rod 9 is carried on crankpin 5 by means of a big-end bearing shell 8.
Shell 8 has a part-peripheral groove 10 in a limited angular region ss, for supplying lubricating oil through a duct 11 in the connecting rod 9 to a piston (not shown). In the example, the angle ss is approximately 90". Bores 6, 7 and 12 are so disposed, relative to the lubricating-oil groove 10, that oil can flow through freely in an angular region of approximately 220cm which is symmetrical with respect to the top dead-centre position of the piston, and the flow of oil to the connecting rod is interrupted in an angular region which is symmetrical with respect to the lower dead-centre point.
The embodiment in Figure 3 differs from Figure 1 in that the bores 6, 7 have part-peripheral lubricating-oil grooves 13 and 14 which are directed towards one another and have a length such that the angle a between them is equal to or less than the angle ss.
WHAT WE CLAIM IS: 1. A reciprocating-piston internal combustion engine comprising means for lubricating a big-end bearing and cooling the associated piston, in which: (a) the associated crankpin is supplied with lubricating oil via bores in the crankshaft and crankpin; (b) the oil is conveyed to the piston via a part-peripheral groove in the big-end bearing shell extending over a limited angular region and subtending an angle ss of less than 1800 at the crankpin axis, the partperipheral groove being connected to a lubricating-oil bore in the associated connecting rod; and (c) at least two radial, angularly-spaced, lubricating-oil bores are provided in the crankpin with the angle a between the two bores, or between the two outer bores where more than two are provided, being less than 1800 at the crankpin axis, the said bores in the crankpin defining an angle of relative rotation between the crankpin and the big-end bearing shell within which the said bores communicate with the partperipheral groove and being so disposed with respect to the part-peripheral groove that the flow of oil is interrupted in a selectable angular region which is symmetrical with respect to the lower dead-centre point; the sum of the angles a and (3being between 280 and 1900 for average piston speeds between 8 and 10 metres per second and
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (4)

**WARNING** start of CLMS field may overlap end of DESC **. selectable angular region which is symmetrical with respect to the lower dead-centre point; the sum of the angles a and p being between 280 and 1900 for average piston speeds between 8 and 10 metres per second and between 240 and 1800 for average piston speeds above 10 metres per second. The present invention is based on the discovery that the average piston speed is related to the optimum oil flow rate; at low piston speeds, a larger peripheral groove is advantageous since it increases the flow rate of oil and, as a result of the lower inertia, a part of the bearing is more lightly stressed, so that a larger groove may be used without disadvantage. At higher piston speeds the optimum oil flow rate is displaced towards lower angular regions, but the region of reduced load capacity is simultaneously reduced by the smaller groove. In addition, the oil flow rate is dependent on the oil pressure, so that the upper tolerance region can be set at a higher lubricating-oil pressure of approximately 7 atmospheres gauge and the lower tolerance region can be set at lubricating-oil pressures of approximately 3 atmospheres gauge. According to a preferred feature of the invention, in order to reduce the region of the bearing shell which is adversely affected by the groove the angle a is greater than the angle P between the two ends of the part-peripheral groove. For this purpose, three radial grooves are provided in the crankpin, with the angle a being subtended by the two outer bores and the third radial lubricating-oil bore dividing the angle a so that both the partial angles are smaller than the angle ss. As an alternative solution, the angle a between the two radial lubricating oil bores is greater than the angle ss between the two ends of the part-peripheral groove, and the crankpin comprises part-peripheral lubricating-oil grooves leading from the radial lubricating-oil bores and directed towards one another, the length of the grooves being such that the angle a sub tended by their ends is equal to or less than the angle ss. Two examples of arrangements in accord ance with the invention are shown in the accompanying drawings, in which: - Figure 1 is a cross-section through an arrangement according to the invention for lubricating a big-end bearing, comprising three radial lubricating-oil bores in the crankpin; and Figure 2 is a cross-section through an arrangement according to the invention for lubricating a big-end bearing having two radial lubricating-oil bores in the crankpin, and groove extensions. A main shaft part 1 of a crankshaft 2 has lubricating-oil bores 3 and 4 through which lubricating oil is supplied to a crankpin 5. Crankpin 5 has radial lubricating-oil bores 6 and 7 whose axes subtend an angle a at the crankpin axis, which angle, in the example shown, is approximately 1300. An additional radial lubricating-oil bore 12 is disposed between bores 6 and 7 and bisects the angle a. A connecting rod 9 is carried on crankpin 5 by means of a big-end bearing shell 8. Shell 8 has a part-peripheral groove 10 in a limited angular region ss, for supplying lubricating oil through a duct 11 in the connecting rod 9 to a piston (not shown). In the example, the angle ss is approximately 90". Bores 6, 7 and 12 are so disposed, relative to the lubricating-oil groove 10, that oil can flow through freely in an angular region of approximately 220cm which is symmetrical with respect to the top dead-centre position of the piston, and the flow of oil to the connecting rod is interrupted in an angular region which is symmetrical with respect to the lower dead-centre point. The embodiment in Figure 3 differs from Figure 1 in that the bores 6, 7 have part-peripheral lubricating-oil grooves 13 and 14 which are directed towards one another and have a length such that the angle a between them is equal to or less than the angle ss. WHAT WE CLAIM IS:
1. A reciprocating-piston internal combustion engine comprising means for lubricating a big-end bearing and cooling the associated piston, in which: (a) the associated crankpin is supplied with lubricating oil via bores in the crankshaft and crankpin; (b) the oil is conveyed to the piston via a part-peripheral groove in the big-end bearing shell extending over a limited angular region and subtending an angle ss of less than 1800 at the crankpin axis, the partperipheral groove being connected to a lubricating-oil bore in the associated connecting rod; and (c) at least two radial, angularly-spaced, lubricating-oil bores are provided in the crankpin with the angle a between the two bores, or between the two outer bores where more than two are provided, being less than 1800 at the crankpin axis, the said bores in the crankpin defining an angle of relative rotation between the crankpin and the big-end bearing shell within which the said bores communicate with the partperipheral groove and being so disposed with respect to the part-peripheral groove that the flow of oil is interrupted in a selectable angular region which is symmetrical with respect to the lower dead-centre point; the sum of the angles a and (3being between 280 and 1900 for average piston speeds between 8 and 10 metres per second and
between 240 and 1800 for average piston speeds above 10 metres per second.
2. An engine according to claim 1 in which three radial bores are provided in the crankpin, the angle a subtended by the axes of the two outer bores being greater than the angle ss, and the third radial lubricatingoil bore dividing the angle a so that both the partial angles are smaller than the angle ss.
3. An engine according to claim 1, in which the angle a is greater than the angle ss, and the crankpin comprises partperipheral lubricating-oil grooves leading from the two said radial lubricating-oil bores and directed towards one another, the length of the grooves being such that the angle a subtended by the adjacent ends of the crankpin grooves is equal to or less than the angle ss.
4. A reciprocating-piston internal combustion engine according to claim 1, substantially as described herein with reference to Figure 1 or Figure 2 of the accompanying drawings.
GB4145877A 1976-10-21 1977-10-05 Arrangement for lubricating a crankpin bearing Expired GB1582075A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19762647441 DE2647441A1 (en) 1976-10-21 1976-10-21 ARRANGEMENT FOR LUBRICATING A CRANK PIN BEARING

Publications (1)

Publication Number Publication Date
GB1582075A true GB1582075A (en) 1980-12-31

Family

ID=5990949

Family Applications (1)

Application Number Title Priority Date Filing Date
GB4145877A Expired GB1582075A (en) 1976-10-21 1977-10-05 Arrangement for lubricating a crankpin bearing

Country Status (4)

Country Link
DE (1) DE2647441A1 (en)
FR (1) FR2368605A1 (en)
GB (1) GB1582075A (en)
IT (1) IT1085050B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2463498A1 (en) * 2009-07-17 2012-06-13 Nissan Motor Co., Ltd. Crankshaft of internal combustion engine provided with multi link-type piston-crank mechanism and multi link-type piston-crank mechanism of internal combustion engine
US20180030864A1 (en) * 2015-08-14 2018-02-01 Bayerische Motoren Werke Aktiengesellschaft Crankshaft Having an Oil Groove

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4345797A (en) * 1978-11-20 1982-08-24 Caterpillar Tractor Co. Lubrication system for an engine
JP3470609B2 (en) * 1998-09-04 2003-11-25 日産自動車株式会社 Internal combustion engine lubrication system
DE102010063191A1 (en) * 2010-12-16 2012-06-21 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine i.e. single-cylinder four-stroke internal combustion engine, for driving motorcycle, has radially running channel directed in position of crankshaft, where axially running channel of engine is part of channels

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2463498A1 (en) * 2009-07-17 2012-06-13 Nissan Motor Co., Ltd. Crankshaft of internal combustion engine provided with multi link-type piston-crank mechanism and multi link-type piston-crank mechanism of internal combustion engine
EP2463498A4 (en) * 2009-07-17 2013-05-29 Nissan Motor Crankshaft of internal combustion engine provided with multi link-type piston-crank mechanism and multi link-type piston-crank mechanism of internal combustion engine
US20180030864A1 (en) * 2015-08-14 2018-02-01 Bayerische Motoren Werke Aktiengesellschaft Crankshaft Having an Oil Groove

Also Published As

Publication number Publication date
FR2368605A1 (en) 1978-05-19
IT1085050B (en) 1985-05-28
DE2647441A1 (en) 1978-04-27
FR2368605B1 (en) 1980-05-16

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Date Code Title Description
PS Patent sealed
PCNP Patent ceased through non-payment of renewal fee