WO2017130457A1 - Bielle et moteur de type à crosse la comprenant - Google Patents

Bielle et moteur de type à crosse la comprenant Download PDF

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Publication number
WO2017130457A1
WO2017130457A1 PCT/JP2016/077761 JP2016077761W WO2017130457A1 WO 2017130457 A1 WO2017130457 A1 WO 2017130457A1 JP 2016077761 W JP2016077761 W JP 2016077761W WO 2017130457 A1 WO2017130457 A1 WO 2017130457A1
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WO
WIPO (PCT)
Prior art keywords
bearing metal
connecting rod
bearing
opening width
oil supply
Prior art date
Application number
PCT/JP2016/077761
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English (en)
Japanese (ja)
Inventor
西田　英朗
拓造 鴫原
Original Assignee
三菱重工業株式会社
株式会社ジャパンエンジンコーポレーション
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 三菱重工業株式会社, 株式会社ジャパンエンジンコーポレーション filed Critical 三菱重工業株式会社
Priority to KR1020187005557A priority Critical patent/KR20180033277A/ko
Priority to CN201680049735.0A priority patent/CN108474410A/zh
Publication of WO2017130457A1 publication Critical patent/WO2017130457A1/fr

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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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/04—Connecting-rod bearings; Attachments thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B77/00—Component parts, details or accessories, not otherwise provided for
    • 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
    • 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
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/02—Constructions of connecting-rods with constant length

Definitions

  • the present invention relates to a connecting rod used for a crosshead engine mounted mainly as a main engine of a ship and a crosshead engine equipped with the connecting rod.
  • FIG. 6 is a longitudinal sectional view of a marine crosshead engine.
  • 7 is a cross-sectional view taken along line VII-VII in FIG. 6
  • FIG. 8 is a plan view taken along line VIII-VIII in FIG. 7
  • FIG. 9 is a vertical cross-sectional view taken along line IX-IX in FIG. is there.
  • a piston 2 is slidably inserted into a cylinder liner 1 extending in the up-down direction
  • a crankshaft 3 is pivotally supported on an axial extension line of the cylinder liner 1, and the cylinder liner 1 and the crankshaft 3
  • a cross head 5 is slidably provided between a pair of sliding plates 4 provided therebetween.
  • a horizontal head-like crosshead journal 7 provided at the tip of a piston rod 6 extending downward from the piston 2 is connected to the crosshead 5. Further, a small end portion 8A of the connecting rod 8 is pivotally attached to the cross head journal 7, and a large end portion 8B of the connecting rod 8 is rotatable to a crank pin 9 provided eccentrically on the crankshaft 3. It is pivotally supported. For this reason, when the piston 2 is pushed down by the explosion pressure P accompanying the combustion of the fuel, the crosshead 5 is also pushed down, the connecting rod 8 rotates to rotate the crankshaft 3, and this rotation is caused by the crosshead type engine EG. Output.
  • Caps 81 and 82 are attached to the small end portion 8A and the large end portion 8B of the connecting rod 8, respectively, so that the crosshead journal 7 and the crank pin 9 are held in a clamped shape. Further, on the bearing surface 8a of the small end portion 8A (81) and the bearing surface 8b of the large end portion 8B (82), halved cylindrical bearing metals 11 and 12 made of a bearing material such as white metal are respectively provided. It is installed.
  • the connecting rod 8 has a small end portion 8A (bearing surface 8a) and a small end portion 8A so as to extend along the internal longitudinal direction.
  • An oil supply passage 15 is formed to communicate with the large end portion 8B (bearing surface 8b).
  • the oil supply passage 15 has holes in the bearing surface 8a of the small end portion 8A and the bearing surface 8b of the large end portion 8B. (See also FIG. 5 in Patent Document 1).
  • the bearing surface 8a has a plurality of oil supply grooves 16 extending along the circumferential direction.
  • the lubricating oil supplied from the lubricating oil pump (not shown) to the crosshead 5 lubricates between the crosshead journal 7 and the bearing metal 11, and then the oil supply groove 16, the oil supply passage 15, and the like. After that, the bearing metal 12 and the crank pin 9 are lubricated.
  • the opening width dimension d of the opening portion of the oil supply passage 15 in the bearing surface 8a of the small end portion 8A is the thickness dimension H of the bearing metal 11. May be larger.
  • the relationship between the opening width dimension d of the recess formed in the bearing surface 8a such as the oil supply passage 15 and the oil supply groove 16 and the thickness dimension H of the bearing metal 11 has not been particularly taken into consideration.
  • the sliding surface 11a of the bearing metal 11 may be damaged, such as uneven wear, and the durability and reliability of the crosshead engine EG may be impaired.
  • the present invention has been made to solve the above-mentioned problems, and while preventing the bearing metal from becoming excessively thick, recesses such as an oil supply passage and an oil supply groove formed on the bearing surface at the end of the connecting rod.
  • This is a connecting rod that suppresses the pressure deformation of the bearing metal due to, eliminates the place where the maximum oil film pressure on the sliding surface of the bearing metal suddenly increases, prevents damage to the bearing metal, and enhances engine durability. It is an object of the present invention to provide a crosshead engine provided.
  • the present invention employs the following means.
  • the connecting rod according to the present invention is a connecting rod that connects between a crosshead journal provided at the tip of a piston rod of a crosshead type engine and a crankpin provided on a crankshaft.
  • the opening width dimension of the recess is d
  • the thickness dimension of the bearing metal is H
  • the relationship of H> d ⁇ ⁇ is satisfied, and the range of the coefficient ⁇ is any of the following.
  • the thickness dimension of the bearing metal formed of a relatively soft bearing material such as white metal is optimized within the minimum necessary range, so that the weight is increased and the cost is increased.
  • the strength of the bearing metal can be increased without incurring.
  • the angle range in which the thickness H of the bearing metal is H> d ⁇ ⁇ is determined from the maximum pressure application point of the explosion pressure applied from the crosshead journal in the circumferential direction of the bearing metal. This is up to a range that does not affect the deformation of the bearing metal, and the thickness dimension of the bearing metal may be smaller than the H in other ranges.
  • the bearing metal since the thickness H of the bearing metal is increased only in the vicinity of the maximum pressure acting point at which the bearing metal is likely to be deformed, and the thickness is not increased in other portions, the bearing metal becomes excessively thick. While preventing this, the pressure deformation of the bearing metal can be suppressed, and the durability of the crosshead engine can be enhanced.
  • the thickness dimension of the bearing metal may change gradually without a step from the maximum portion to the minimum portion. As a result, there is no portion where the cross-sectional shape of the bearing metal changes abruptly, and the concentration of stress and metal fatigue can be avoided to extend the life of the bearing metal, and the durability of the crosshead engine can be enhanced.
  • crosshead type engine according to the present invention includes any one of the connecting rods described above, it is possible to prevent the pressure deformation of the bearing metal and improve the engine durability.
  • the connecting rod according to the present invention and the crosshead engine equipped with the connecting rod are formed on the bearing surface at the end of the connecting rod while preventing the bearing metal from becoming excessively thick. Suppresses bearing metal pressure deformation due to recesses such as oil supply passages and oil supply grooves, eliminates places where the maximum oil film pressure suddenly increases on the sliding surface of the bearing metal, prevents damage to the bearing metal, and improves engine durability be able to.
  • FIG. 1B is a longitudinal sectional view taken along line Ib-Ib in FIG. 1A.
  • FIG. 1B is a longitudinal sectional view taken along line Ic-Ic in FIG. 1B.
  • It is a graph which shows the deformation amount of the bearing metal by the relationship between the thickness of a bearing metal, and the opening width dimension of the recessed part in a bearing surface. While showing 2nd Embodiment of this invention, it is a side view of the connecting rod which shows the angle range which enlarges the thickness dimension of a bearing metal.
  • FIG. 7 is a longitudinal sectional view of a piston rod and a connecting rod along the line VII-VII in FIG. 6 showing a conventional technique.
  • FIG. 8 is a plan view of a bearing surface of a connecting rod as viewed in the direction of arrows VIII-VIII in FIG. 7 showing a conventional technique.
  • FIG. 8 is a longitudinal sectional view of a connecting rod taken along line IX-IX in FIG. 7 showing a conventional technique.
  • the connecting rod 18 shown here is provided with a small end portion 8A similar to the conventional connecting rod 8 shown in FIGS. 8 and 9, and a cap 81 is attached to the small end portion 8A, and a cross provided on the piston side.
  • a head journal (see reference numeral 7 in FIG. 6) is rotatably held.
  • Half-cylindrical bearing metals 11A and 11B are mounted on the bearing surface 8a.
  • a bearing metal 11A is mounted on the small end portion 8A side, and a bearing metal 11B is mounted on the cap 81 side.
  • an oil supply passage 15 (concave portion) extending along the longitudinal direction (the axial direction of the connecting rod 18) is formed. Further, for example, three oil supply grooves 16 (concave portions) are formed in the bearing surface 8a along the circumferential direction.
  • the oil supply passage 15 is connected to, for example, a central oil supply groove 16.
  • the inner diameter (opening diameter) of the oil supply groove 16 is larger than the width of the oil supply groove 16, but this magnitude relationship may be reversed or equivalent.
  • the opening width dimension of the recess formed in the bearing surface 8a such as the oil supply passage 15 and the oil supply groove 16 is d and the thickness dimension of the bearing metal 11A is H
  • H> d ⁇ ⁇ H is set so that ⁇ is a coefficient.
  • the range of the coefficient ⁇ is set based on any of the following conditions (a) to (d).
  • the coefficient ⁇ is 0.8 because it corresponds to the above condition (b).
  • marine diesel engines are usually designed so that the oil film pressure between the crosshead journal 7 and the bearing metals 11A and 11B during operation is 60 MPa or less.
  • the thickness of the oil film is as small as approximately 5 ⁇ m or less.
  • the deformation of the bearing metal 11A due to the explosion pressure P causes the point E where the distribution state of the maximum oil film pressure rises abruptly to prevent lubrication failure due to the thin oil film.
  • FIG. 2 is a graph showing the deformation amount of the bearing metal 11A according to the relationship between the thickness dimension H of the bearing metal 11A and the opening width dimension d of the recess in the bearing surface 8a.
  • the vertical axis represents the ratio H / d between the thickness dimension H and the opening width dimension d of the bearing metal 11A, that is, the thickness coefficient ⁇ of the bearing metal 11A, and the horizontal axis represents the opening width dimension d.
  • the maximum oil film pressure is assumed to be a normal value of 60 MPa.
  • the amount of deformation of the bearing metal 11A is made smaller than the oil film thickness between the cross head journal 7 and the bearing metals 11A and 11B, thereby reducing the oil film pressure while minimizing the thickness dimension H of the bearing metal 11A. Can be suppressed.
  • the value of H / d that is, the coefficient ⁇ is set so that the deformation amount of the bearing metal 11A is smaller than 5 ⁇ m that is the thickness of the oil film, preferably 1 ⁇ m or less. That is, according to the opening width dimension d, the coefficient ⁇ is set so as to approximate the boundary line having a deformation amount of 1 ⁇ m shown in FIG. 2, and the thickness dimension H of the bearing metal 11A is determined.
  • the diagram (deformation amount) shown in FIG. 2 can be calculated by FEM analysis or theoretical calculation of a beam model.
  • the thickness coefficient ⁇ is set to 0.8, and the thickness dimension of the bearing metal 11A from the relationship of H> d ⁇ ⁇ . H may be set. At this time, it is preferable to set the lower limit value of the thickness coefficient ⁇ to 0.6 or more so that the thickness dimension H does not become too thin.
  • the thickness coefficient ⁇ may be selected from the width dimension d in the range of 0.8 to 1.2, and the thickness dimension H of the bearing metal 11A may be set from the relationship of H> d ⁇ ⁇ .
  • the thickness coefficient ⁇ of the bearing metal 11A is determined in the range of 0.5 to 0.6, and is described above.
  • the thickness dimension H of the bearing metal 11A may be set from the above formula. This is because the recess H is formed only in the hole of the oil supply passage 15, that is, when the oil supply groove 16 is not formed, the thickness dimension H of the bearing metal 11 ⁇ / b> A is set thinner than when both are formed. This is because it can be done. That is, it is a range in consideration of the fact that the thickness dimension H of the bearing metal 11A does not become too thin in practice.
  • the thickness coefficient ⁇ is determined in the range of 0.6 to 0.8, and the thickness of the bearing metal 11A is calculated from the above formula. What is necessary is just to set a dimension.
  • the thickness dimension H of the bearing metal 11A can be set thinner than when both the oil supply passage 15 and the oil supply groove 16 are formed.
  • the thickness H of the bearing metal 11A formed of a relatively soft bearing material such as white metal is optimized within a necessary minimum range.
  • the strength of the bearing metal 11A can be increased without causing an increase in weight or an increase in cost.
  • the bearing metal 11A is formed by the recesses such as the oil supply passage 15 and the oil supply groove 16 formed in the bearing surface 8a of the small end portion 8A of the connecting rod 18. It is possible to suppress pressure deformation, eliminate a place where the maximum oil film pressure on the sliding surface 11a of the bearing metal 11A is rapidly increased, prevent the bearing metal 11A from being damaged, and improve the durability of the crosshead type engine EG.
  • the thickness dimension H of the bearing metal 11A is calculated from the equation H> d ⁇ ⁇ , as in the case of the first embodiment.
  • the angle range ⁇ that is the thickness dimension H is a range that does not affect the deformation of the bearing metal 11A in the circumferential direction of the bearing metal 11A when the position of the maximum pressure application point Pmax is 0 degree. For example, it is limited only to a range of ⁇ 30 degrees. In a range other than the angle range ⁇ , the thickness dimension of the bearing metal 11A is smaller than H. That is, the thickness of the bearing metal in the conventional connecting rod is maintained.
  • the surface pressure applied from the crosshead journal 7 is highest at the point where the maximum pressure application point Pmax is applied, that is, 0 degree, but when it exceeds ⁇ 30 degrees from this point, the deformation of the bearing metal 11A occurs. Decrease to an unaffected level.
  • the thickness H of the bearing metal 11A is increased only in the range from the maximum pressure application point Pmax at which the bearing metal 11A is likely to be deformed to ⁇ 30 degrees, and the thickness is not increased in other portions. While preventing the metal 11A from becoming excessively thick, the pressure deformation of the bearing metal 11A can be suppressed, and the durability of the crosshead type engine EG can be enhanced.
  • the connecting rod 38 has the same configuration as the connecting rod 18 shown in FIG. 1C and the connecting rod 28 shown in FIG. 3 except for the shape of the bearing metal 11A.
  • the maximum thickness dimension H in the vicinity of the center portion of the bearing metal 11A is H> d ⁇ described in the first embodiment with respect to the opening width dimension d of the oil supply passage 15 opening in the bearing surface 8a.
  • the thickness H is calculated from the formula of ⁇ , and the thickness H decreases from the vicinity of the center to both ends.
  • the thickness H of the bearing metal 11A is gradually changed without a step from the maximum portion to the maximum size.
  • the bearing metal 11A does not have a portion where the cross-sectional shape changes suddenly, avoids stress concentration and concentration of metal fatigue, extends the life of the bearing metal 11A, and improves the durability of the crosshead type engine EG.
  • the curvature of the bearing surface 8a is the same as that of the conventional one shown in FIG. 9, and the depth of the bearing surface 8a is simply dug down by the amount obtained by subtracting the minimum thickness dimension from the maximum thickness dimension H of the bearing metal 11A. Since it is good, it can manufacture, without changing the conventional manufacturing process largely.
  • the connecting rods 11A are prevented from becoming excessively thick.
  • the pressure deformation of the bearing metal 11A due to the recesses such as the oil supply passage 15 and the oil supply groove 16 formed in the bearing surface 8a of the small end portion 8A of 18, 28, 38 is suppressed, and the maximum in the sliding surface 11a of the bearing metal 11A It is possible to prevent the bearing metal 11A from being damaged by eliminating a place where the oil film pressure rapidly increases, and to improve the durability of the engine.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

La présente invention concerne la suppression de déformation de pression d'un métal pour palier provoquée par des parties évidées telles qu'un trajet d'alimentation en huile ou une rainure d'alimentation en huile formé(e) dans une surface de palier au niveau d'une extrémité d'une bielle, tout en évitant que le métal pour palier ne soit excessivement épaissi. L'invention concerne une bielle (18) comprenant des parties évidées (15, 16) qui sont formées dans une surface de palier (8a) d'une extrémité (8A) de la bielle (18) et un métal pour palier (11A) qui est fixé à la surface de palier (8a) et qui présente une forme semi-cylindrique. Lorsque la dimension de largeur d'ouverture de chacune des parties évidées (15, 16) est définie comme d et que la dimension d'épaisseur du métal pour palier (11A) est définie comme H, H est défini pour satisfaire H>d·α et la plage du coefficient α est définie de manière à satisfaire l'une quelconque des équations suivantes : (a) α>0,6 au cas où les parties évidées sont un trou et des rainures et la dimension de largeur d'ouverture d est inférieure à 10 mm ; (b) α=0,8 au cas où les parties évidées sont un trou et des rainures et la dimension de largeur d'ouverture d est 10-40 mm ; (c) α>0,5 au cas où toutes les parties évidées sont des trous et la dimension de largeur d'ouverture d est inférieure à 10 mm ; et (d) α>0,6 au cas où toutes les parties évidées sont des trous et la dimension de largeur d'ouverture d est 10-40 mm.
PCT/JP2016/077761 2016-01-25 2016-09-21 Bielle et moteur de type à crosse la comprenant WO2017130457A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
KR1020187005557A KR20180033277A (ko) 2016-01-25 2016-09-21 연접봉 및 이것을 구비한 크로스헤드형 엔진
CN201680049735.0A CN108474410A (zh) 2016-01-25 2016-09-21 连接棒及具有连接棒的十字头式发动机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-011904 2016-01-25
JP2016011904A JP2017133541A (ja) 2016-01-25 2016-01-25 連接棒およびこれを備えたクロスヘッド型エンジン

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WO2017130457A1 true WO2017130457A1 (fr) 2017-08-03

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PCT/JP2016/077761 WO2017130457A1 (fr) 2016-01-25 2016-09-21 Bielle et moteur de type à crosse la comprenant

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JP (1) JP2017133541A (fr)
KR (1) KR20180033277A (fr)
CN (1) CN108474410A (fr)
WO (1) WO2017130457A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110159646A (zh) * 2018-02-15 2019-08-23 丰田自动车株式会社 连杆

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6348017U (fr) * 1986-09-17 1988-04-01
JPH09144759A (ja) * 1995-11-22 1997-06-03 Mitsubishi Heavy Ind Ltd すべり軸受装置
JPH11230170A (ja) * 1998-02-13 1999-08-27 Daido Metal Co Ltd すべり軸受
JP2007532845A (ja) * 2004-05-18 2007-11-15 エムエーエヌ・ディーゼル・エーエス 大型２サイクルディーゼルエンジン用クロスヘッド軸受

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6348017U (fr) * 1986-09-17 1988-04-01
JPH09144759A (ja) * 1995-11-22 1997-06-03 Mitsubishi Heavy Ind Ltd すべり軸受装置
JPH11230170A (ja) * 1998-02-13 1999-08-27 Daido Metal Co Ltd すべり軸受
JP2007532845A (ja) * 2004-05-18 2007-11-15 エムエーエヌ・ディーゼル・エーエス 大型２サイクルディーゼルエンジン用クロスヘッド軸受

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110159646A (zh) * 2018-02-15 2019-08-23 丰田自动车株式会社 连杆
CN110159646B (zh) * 2018-02-15 2022-05-03 丰田自动车株式会社 连杆

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CN108474410A (zh) 2018-08-31
JP2017133541A (ja) 2017-08-03
KR20180033277A (ko) 2018-04-02

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