WO2016157575A1 - Bielle et moteur du type à crosse comportant cette dernière - Google Patents

Bielle et moteur du type à crosse comportant cette dernière Download PDF

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Publication number
WO2016157575A1
WO2016157575A1 PCT/JP2015/077605 JP2015077605W WO2016157575A1 WO 2016157575 A1 WO2016157575 A1 WO 2016157575A1 JP 2015077605 W JP2015077605 W JP 2015077605W WO 2016157575 A1 WO2016157575 A1 WO 2016157575A1
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WO
WIPO (PCT)
Prior art keywords
connecting rod
oil supply
bearing surface
opening
diameter portion
Prior art date
Application number
PCT/JP2015/077605
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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
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 filed Critical 三菱重工業株式会社
Priority to CN201580077620.8A priority Critical patent/CN107407323B/zh
Priority to KR1020177023819A priority patent/KR101957622B1/ko
Publication of WO2016157575A1 publication Critical patent/WO2016157575A1/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
    • 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
    • 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
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/04—Connecting-rod bearings; Attachments thereof

Definitions

  • the present invention relates to a connecting rod used in a crosshead type engine mounted mainly as a main ship of a ship, and a crosshead type engine provided with the same.
  • FIG. 6 is a longitudinal sectional view of a crosshead type engine for ships.
  • 7 is a sectional view taken along the line VII-VII in FIG. 6
  • FIG. 8 is a plan view taken along the line VIII-VIII in FIG. 7
  • FIG. 9 is a longitudinal sectional view taken along the line IX-IX in FIG.
  • the piston 2 is slidably inserted in the cylinder liner 1 extending in the vertical direction
  • the crankshaft 3 is axially supported on the axis center extension line of the cylinder liner 1.
  • the cross head 5 is provided slidably in the vertical direction between a pair of sliding plates 4 provided therebetween.
  • a crosshead-like crosshead journal 7 provided at the end of a piston rod 6 extending downward from the piston 2 is connected to the crosshead 5.
  • the small end 8A of the connecting rod 8 is pivotally mounted on the cross head journal 7 and the large end 8B of the connecting rod 8 is rotatable on a crank pin 9 provided eccentrically to the crankshaft 3. It is pivotally supported. Therefore, when the piston 2 is depressed by the pressure P accompanying the combustion of the fuel, the crosshead 5 is also depressed and the connecting rod 8 is rotated to rotate the crankshaft 3, and this rotation is an output of the crosshead type engine EG. It becomes.
  • Caps 81 and 82 are attached to the small end 8A and the large end 8B of the connecting rod 8, respectively, so that the cross head journal 7 and the crank pin 9 are held in a clamp shape.
  • Half cylindrical bearing metals 11, 12 formed of a bearing material such as white metal are mounted on the bearing surface 8a of the small end 8A (81) and the bearing surface 8b of the large end 8B (82). ing.
  • the connecting rod 8 is shown in FIG. 6 with a small end 8A (bearing surface 8a) so as to extend along its internal longitudinal direction.
  • An oil supply passage 15 is formed to communicate with the large end 8B (bearing surface 8b).
  • the oil supply passage 15 communicates with the bearing surface 8a of the small end 8A and the bearing surface 8b of the large end 8B (see also FIG. 5 of Patent Document 1).
  • the bearing surface 8a is formed with a plurality of oil supply grooves 16 extending along the circumferential direction.
  • the inner diameter of the opening of the oil supply passage 15 at the bearing surface 8a of the small end 8A is larger than the width of the oil supply groove 16. .
  • the opening position of the oil supply passage 15 corresponds to the central portion of the bearing surface 8a, that is, the center line C of the connecting rod 8 (see FIGS. 8 and 9).
  • the inner diameter of the opening of the oil supply passage 15 is larger than the width of the oil supply groove 16, and the opening of the oil supply passage 15 is located at the central portion of the bearing surface 8a. For this reason, in the pressure range R in which the pressure P (see FIG. 6) applied from the cross head journal 7 is the highest, the opening of the oil passage 15 and the oil groove 16 overlap and the back surface of the bearing metal 11 is The area of the non-contacting part was large.
  • the oil film of the lubricating oil supplied between the sliding surface 11a of the bearing metal 11 and the crosshead journal 7 Becomes thinner. Therefore, damage such as uneven wear may occur on the sliding surface 11a of the bearing metal 11, 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 it is an object of the present invention to provide a connecting rod capable of suppressing damage to bearing metals and enhancing engine durability and a crosshead type engine including the connecting rod. Do.
  • the present invention adopts the following means.
  • the connecting rod according to the first aspect of the present invention is for connecting between a crosshead journal provided at the end of a piston rod of a crosshead type engine and a crank pin provided on a crankshaft.
  • An oil supply passage is formed to extend along the longitudinal direction inside the connecting rod and is connected to the bearing surface of the end of the connecting rod, and is formed to extend along the circumferential direction of the bearing surface.
  • An oil supply groove connected to an opening opened on a bearing surface, and a half-cylindrical bearing metal mounted on the bearing surface, the position of the opening of the oil supply passage being the bearing surface
  • the pressure applied from the crosshead journal is circumferentially outside the highest pressure range.
  • the opening of the oil supply passage opened to the bearing surface at the end is located at the circumferentially outer side with respect to the pressure range in which the pressure applied from the cross head journal is the highest. For this reason, as in the conventional connecting rod, the opening of the oil supply passage is located in the pressure range, and there is no part where the bearing surface does not contact the back surface of the bearing metal in the pressure range.
  • a connecting rod is for connecting between a crosshead journal provided at the end of a piston rod of a crosshead type engine and a crank pin provided at a crankshaft, the connecting rod And an oil supply passage extending in the longitudinal direction along the longitudinal direction of the connecting rod and connected to the bearing surface at the end of the connecting rod, and the oil supply passage extending along the circumferential direction of the bearing surface.
  • An oil supply groove connected to the opening opening upward and a half cylindrical bearing metal mounted on the bearing surface are provided, and the inner diameter of the opening of the oil supply passage is set equal to or less than the width dimension of the oil supply groove It is done.
  • the opening of the oil supply passage opened to the bearing surface at the end thereof is opened to the inside of the oil supply groove formed along the circumferential direction of the bearing surface, and the opening of the oil supply passage
  • the inner diameter of is set equal to or less than the width dimension of the oil supply groove. Therefore, as in the conventional case, the opening of the oil supply passage having an inner diameter larger than the width of the oil supply groove is present in the pressure range together with the oil supply groove, thereby increasing the area not contacting the back surface of the bearing metal in the pressure range.
  • the oil supply groove is formed on the bearing surface at a circumferentially outer position with respect to a pressure range in which the pressure applied from the cross head journal is the highest.
  • the oil supply passage is branched from the large diameter portion extending along the longitudinal direction of the inside of the connecting rod and the end portion of the large diameter portion to communicate with the bearing surface and from the large diameter portion
  • a plurality of small diameter portions having a small inner diameter may be provided, and a tip of each of the small diameter portions may be the opening in the bearing surface.
  • the inner diameters of the plurality of small diameter portions are made different from each other, and in the bearing surface, the inner diameter of the small diameter portion located within the pressure range in which the pressure applied from the cross head journal is highest is It may be smaller than the inner diameter of the small diameter portion located at a place other than the above.
  • the plurality of small diameter portions may be branched from the large diameter portion at different angles.
  • the large diameter portion is preferably structurally located in the middle of the cross sectional area of the connecting rod.
  • the end of each small diameter portion can be relatively freely opened at an arbitrary position on the bearing surface with respect to the large diameter portion whose arrangement position is restricted. For this reason, the position of the opening in the bearing surface of each small diameter portion can be optimized, the pressure deformation of the bearing metal can be suppressed, and the durability of the crosshead type engine can be enhanced.
  • a plurality of the oil supply passages may be formed in parallel, and the openings of each of them may be communicated with different places of the bearing surface.
  • each oil supply passage can be reduced and the area of each opening can be reduced without reducing the overall amount of oil supply, thereby suppressing the occurrence of pressure deformation such that the bearing metal enters the opening.
  • a connecting rod is for connecting between a crosshead journal provided at the end of a piston rod of a crosshead type engine and a crank pin provided at a crankshaft, the connecting rod
  • An oil supply passage formed to extend along the longitudinal direction of the inside of the cylinder, an oil supply groove formed to extend along the circumferential direction of the bearing surface at the end of the connecting rod, and the bearing surface attached
  • the bearing passage side is in communication with the bottom of the oil supply groove without reaching the bearing surface.
  • the oil supply passage since the oil supply passage does not directly communicate with the bearing surface but communicates with the bottom of the oil groove formed in the bearing surface, only the oil groove is present as a recess in the bearing surface There is no recess other than the above.
  • the lubricating oil collected in the oil supply groove can flow from the opening formed by the bottom of the oil supply groove and the end of the oil supply passage to the oil supply passage.
  • crosshead type engine according to the present invention includes any one of the connecting rods described above, pressure deformation of the bearing metal can be suppressed to improve engine durability.
  • (a) is a top view of the bearing surface of a connecting rod
  • (b) is a longitudinal cross-sectional view of a connecting rod in alignment with the IIIb-IIIb line of (a).
  • (a) is a top view of the bearing surface of a connecting rod
  • (b) is a longitudinal cross-sectional view of a connecting rod in alignment with the IVb-IVb line of (a).
  • FIG. 1 is a longitudinal sectional view of a marine crosshead engine.
  • FIG. 7 is a longitudinal sectional view of a piston rod and a connecting rod taken along the line VII-VII of FIG. 6 showing a prior art. It is a top view of the bearing surface of a connecting rod by the VIII-VIII arrow of FIG. 7 which shows a prior art.
  • FIG. 8 is a longitudinal cross-sectional view of a connecting rod taken along line IX-IX of FIG. 7 showing the prior art.
  • FIGS. 1 (a) and 1 (b) a connecting rod according to a first embodiment of the present invention will be described with reference to FIGS. 1 (a) and 1 (b).
  • the connecting rod 18 shown here has the same small end 8A as the conventional connecting rod 8 shown in FIGS. 8 and 9, and a cap (see 81 in FIG. 6) not shown is attached to the small end 8A.
  • the cross head journal (see reference numeral 7 in FIG. 6) provided on the piston side is rotatably held.
  • a cylindrical bearing metal 11 is mounted on the bearing surface 8a (not shown in FIG. 1A).
  • An oil supply passage 15 is formed inside the connecting rod 18, and an oil supply groove 16 extending along the circumferential direction is formed in the bearing surface 8a (three sides on each side of the center line C of the connecting rod 18 in this embodiment) A total of 6) are formed.
  • the oil supply passage 15 has a circular hole-shaped large diameter portion 15a extending along the longitudinal direction of the inside of the connecting rod 18, and a V shape so as to sandwich the center line C of the connecting rod 18 from the end of the large diameter portion 15a.
  • the tip portions (openings 15 c) of the respective small diameter portions 15 b are respectively connected to the oil supply grooves 16 on both sides of the center line C of the connecting rod 18.
  • the inner diameter of the opening 15 c in the present embodiment is larger than the width of the oil supply groove 16, but may be equal to or less than the width of the oil supply groove 16.
  • the pressure acts on the portion where the bearing surface 8a of the connecting rod 18 and the cross head journal 7 (see FIG. 6) contact, by the vertical movement of the piston 2.
  • the high pressure range pressure range
  • the high pressure range varies depending on the size of the engine, but at least the axial axial lowermost position where the crosshead journal 7 and the bearing surface 8a of the connecting rod 18 are in contact (connecting rod 18 Is a range including at least 120.degree. Across the center line C if it moves within a range of 120.degree. About the cross head journal.
  • the highest pressure P exerted from the cross head journal 7 on the bearing surface 8a is in the range of R shown in the drawing.
  • the position of this pressure range R is circumferentially offset from the center line C of the connecting rod 18. The reason is that, as shown in FIG. 6, when the piston 2 is started to be depressed by the pressure P accompanying the combustion of fuel, the crankshaft 3 comes from the top dead center position of the piston 2 to a rotation angle ⁇ of about 20 ° This is because the largest pressure is applied when the rod 18 is inclined.
  • the range in which the pressure P acts the highest is defined as the pressure range R, but a relatively high range of pressure may be set as the pressure range.
  • neither the small diameter portion 15b (opening 15c) of the oil supply passage 15 nor the oil supply groove 16 is formed in the pressure range R described above.
  • the opening 15c of the small diameter portion 15b is at a position circumferentially outside with respect to the pressure range R, and is open at one end of the center of the three oil grooves 16 interrupted at this position. .
  • the small diameter portion 15b branched in a V shape from the upper end of the large diameter portion 15a of the oil supply passage 15 branches from the large diameter portion 15a at different angles ⁇ and ⁇ , respectively.
  • the range in which the pressure P acts the highest is defined as the pressure range R, and the pressure range R is offset from the center line C in the circumferential direction.
  • the small diameter portion 15 b is branched from the oil supply passage 15 at different angles ⁇ and ⁇ .
  • the opening 15 c opens near the circumferential outer side of the pressure range R, it may be considered to make the angles ⁇ and ⁇ equal.
  • lubricating oil is supplied to the crosshead 5 from a lubricating oil pump (not shown).
  • This lubricating oil lubricates between the cross head journal 7 and the sliding surface 11a of the bearing metal 11, passes through an oil hole (not shown) bored in the bearing metal 11, and enters the oil feeding groove 16, and further the opening 15c.
  • the position of the opening 15c of the oil supply passage 15 opened on the bearing surface 8a is circumferentially outside with respect to the pressure range R of the bearing surface 8a. Therefore, as in the conventional connecting rod 8 (see FIGS. 8 and 9), the bearing surface 8a does not occur on the back surface of the bearing metal 11 in the pressure range R when the opening 15c is positioned in the pressure range R. .
  • the oil supply groove 16 formed in the bearing surface 8 a is formed at a circumferentially outer position with respect to the pressure range R. For this reason, when the load (pressure P) of the cross head journal 7 acts on the bearing metal 11, it is possible to suppress pressure deformation due to the bearing metal 11 entering the recess of the oil supply groove 16. Therefore, it is possible to suppress the occurrence of damage such as uneven wear on the sliding surface 11a of the bearing metal 11, and to improve the durability of the crosshead type engine EG.
  • the oil supply passage 15 includes a large diameter portion 15a extending along the longitudinal direction inside the connecting rod 18, and a small diameter portion 15b branched from an end of the large diameter portion 15a and leading to the bearing surface 8a.
  • the tip of each of 15b is an opening 15c in the bearing surface 8a.
  • two or more small diameter portions 15b are branched from one large diameter portion 15a and opened at a plurality of positions on the bearing surface 8a to reduce the amount of oil passing through the oil supply passage 15. Instead, the area of the individual openings 15c can be reduced. As a result, even if the opening 15 c opens into the pressure range R, for example, due to design considerations, the opening area can be minimized.
  • the plurality of small diameter portions 15b are branched from the large diameter portion 15a at different angles ⁇ and ⁇ respectively, the end of each small diameter portion 15b with respect to the large diameter portion 15a having a restriction on the arrangement position
  • the part can be relatively freely opened at any position of the bearing surface 8a. Therefore, the position of the opening 15c in the bearing surface 8a can be optimized, the pressure deformation of the bearing metal 11 can be suppressed, and the durability of the crosshead type engine EG can be enhanced.
  • the oil supply passage 15 is branched from the end of the large diameter portion 15a and the large diameter portion 15a formed in a circular hole shape so as to extend along the longitudinal direction inside the connecting rod 28.
  • a plurality of small diameter portions 15b communicating with the bearing surface 8a are provided, and the tip of each small diameter portion 15b is an opening 15c in the bearing surface 8a.
  • a total of six small diameter portions 15b are formed, three on each side of the center line C of the connecting rod 18.
  • the small diameter portions 15b which are branched in a V shape from the upper end of the large diameter portion 15a to form the above two groups have the center line C as in the case of the first embodiment. It extends at a different angle to the
  • the three small diameter portions 15b are open inside the pressure range R, and the other three small diameter portions 15b are open outside the pressure range R.
  • the small diameter portion 15b opened to the inside of the pressure range R is opened at the tip of the three oil grooves 16 formed in the same manner as the first embodiment, and the inner diameter of the opening 15c is the same as that of the oil groove 16 It is set equal to or less than the width dimension.
  • the small diameter portion 15b opened to the outside of the pressure range R is also open at the tips of the three oiling grooves 16 on the opposite side, and the inner diameter of the opening 15c is set larger than the width dimension of the oiling groove 16 ing.
  • the openings 15 c of the six small diameter portions 15 b of the oil supply passage 15 opening on the bearing surface 8 a have two large and small inner diameters. Further, the inner diameter of the opening 15 c located in the pressure range R of the bearing surface 8 a is smaller than the inner diameter of the small diameter portion 15 b located outside the pressure range R, and the inner diameter is equal to the width dimension of the oil groove 16. It is set equal to or less than.
  • the oil supply passage 15 having an inner diameter larger than the width of the oil supply groove 16 is present in the pressure range R together with the oil supply groove 16. There is no increase in the area not in contact with the back surface of the bearing metal 11 in the middle. Therefore, when the load (pressure P) of the cross head journal 7 acts on the bearing metal 11, it is possible to suppress the occurrence of pressure deformation so that the bearing metal 11 enters the opening 15c of the small diameter portion 15b. As a result, the occurrence of damage such as uneven wear on the sliding surface 11 a of the bearing metal 11 can be suppressed, and the durability of the crosshead engine EG can be enhanced.
  • FIGS. 3 (a) and 3 (b) a connecting rod according to a third embodiment of the present invention will be described with reference to FIGS. 3 (a) and 3 (b).
  • the connecting rod 38 two circular oil supply passages 15A and 15B are formed in parallel with each other, and the openings 15c of the two oil supply passages 15A and 15B are different places of the bearing surface 8a. It is in communication with Specifically, the pressure range is such that the two openings 15c are spaced apart in the circumferential direction of the bearing surface 8a with respect to the center line C of the connecting rod 8, and sandwich the pressure range R of the bearing surface 8a. It is disposed at a position circumferentially outside with respect to R.
  • the oil supply grooves 16 (three in each side across the center line C of the connecting rod 18 in the present embodiment, six in total in the present embodiment) are formed outside the pressure range R.
  • the opening 15 c of the oil supply passage 15 A, 15 B is in communication with the tip of the oil supply groove 16 at the center.
  • the inner diameter of the opening 15 c is preferably set equal to or less than the width dimension of the oil supply groove 16.
  • the oil supply passages 15A and 15B having two equal inner diameters are formed in parallel inside thereof, and the openings 15c of the oil supply passages 15A and 15B are different from the bearing surface 8a. It communicates with the place. Therefore, the inner diameter of each of the oil supply passages 15A and 15B can be reduced without reducing the overall amount of oil supply, and the area of each of the openings 15c can be reduced.
  • the oil supply passages 15A and 15B communicate circumferentially outward with respect to the pressure range R of the bearing surface 8a. Since the inner diameter of the opening 15c is set equal to or less than the width dimension of the oil supply groove 16 and the oil supply groove 16 is not formed in the pressure range R, There is no recess on the back surface where the bearing surface 8a does not contact.
  • the inner diameters of the oil supply passages 15A and 15B can be reduced as described above, the reduction in strength of the connecting rod 8 caused by the formation of the oil supply passages 15A and 15B can be suppressed. Can be enhanced.
  • the two oil supply passages 15A and 15B are formed parallel to the center line C of the connecting rod 38, so that their processing is easy. Two or more fuel supply passages 15A, 15B may be formed, or the inner diameters may be made different.
  • the oil supply passage 15 branches from the end portion of the large diameter portion 15a having a circular hole shape extending along the longitudinal direction inside the connecting rod 28, and leads to the bearing surface 8a.
  • a plurality of small diameter portions 15 b are combined and configured.
  • the tip of each small diameter portion 15b is an opening 15c in the bearing surface 8a.
  • the number of the small diameter portions 15b is, for example, four and radially extends from the large diameter portion 15a, and the respective openings 15c are opened at a plurality of locations on the bearing surface 8a. ing. More specifically, all of the openings 15c are open to the inside of the three oil supply grooves 16 formed in the circumferential direction of the bearing surface 8a. Three openings 15 c are opened in the center oil supply groove 16, and one opening 15 c is opened in the oil supply grooves 16 on both sides.
  • the inner diameter of each small diameter portion 15 b (opening 15 c) is set equal to or smaller than the width dimension of the oil supply groove 16. It is not necessary to open all the openings 15 c in the oil supply groove 16, and only a part of the openings 15 c may be opened in the oil supply groove 16.
  • the connecting rod 48 configured in this way branches a large number of small diameter portions 15b from one large diameter portion 15a and opens it at a plurality of positions on the bearing surface 8a, the amount of oil passing through the oil supply passage 15 The area of the individual openings 15c can be reduced without reduction.
  • openings 15 c are disposed within the pressure range R of the bearing surface 8 a, but each opening 15 c is open to the inside of the oil supply groove 16, and the inner diameter is set equal to or less than the width dimension of the oil supply groove 16 Therefore, the opening 15 c whose inner diameter is larger than the width of the oil supply groove 16 does not open into the pressure range R.
  • the connecting rod 58 is formed, for example, with three oil grooves 16 extending along the circumferential direction on the bearing surface 8a of the small end 8A, and the central groove is formed deeper than the grooves on both sides It is done.
  • a circular oil supply passage 15 is formed in the inside of the connecting rod 58 so as to extend along the longitudinal direction, and the end of the oil supply passage 15 on the bearing surface 8 a side reaches the bearing surface 8 a It does not communicate with the bottom of the central oil supply groove 16. For this reason, a slit-like opening 15 c communicating with the oil supply passage 15 is formed at the center of the central oil supply groove 16 in the longitudinal direction.
  • the length of the opening 15 c is equal to the inner diameter of the oil supply passage 15, and the width of the opening 15 c is equal to the width of the oil supply groove 16.
  • the oil supply passage 15 is disposed to overlap the pressure range R of the bearing surface 8a, this oil supply passage Since the reference numeral 15 does not directly communicate with the surface of the bearing surface 8a but communicates only with the bottom of the oil supply groove 16, the oil supply passage 15 is not exposed as a recess in the bearing surface 8a. For this reason, only three oil supply grooves 16 are present as recesses in the bearing surface 8a, and no other recesses are present.
  • the lubricating oil collected in the oil supply groove 16 can flow to the oil supply passage 15 from an opening 15 c formed by overlapping the bottom of the oil supply groove 16 at the center and the end of the oil supply passage 15.
  • the bearing surface of the end 8A of the connecting rods 18 to 58 By suppressing the pressure deformation of the bearing metal 11 due to the formation of the recess by the oil supply passage 15 communicating with 8a, there is no place where the maximum oil film pressure on the sliding surface 11a of the bearing metal 11 rapidly increases. It is possible to suppress the occurrence of damage such as wear and to improve the durability of the engine.
  • the present invention is not limited only to the configuration of the above embodiment, and can be appropriately modified or improved, and an embodiment with such modification or improvement is also included in the scope of the present invention. .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne une bielle (18) qui relie un tourillon de crosse (7) et un maneton (9) d'un moteur du type à crosse (EG) et la bielle comprend : un trajet d'alimentation en huile (15) qui est formé de sorte à s'étendre dans la direction longitudinale de la partie intérieure de la bielle et qui rejoint une surface d'appui (8a) d'une section d'extrémité (8A) ; une rainure d'alimentation en huile (16) qui est formée de sorte à s'étendre dans la direction circonférentielle de la surface d'appui (8a) et qui rejoint une ouverture (15c) où le trajet d'alimentation en huile (15) s'ouvre sur la surface d'appui (8a) ; et un métal antifriction (11) qui est fixé à la surface d'appui (8a) et qui a une forme semi-cylindrique. L'emplacement de l'ouverture (15c) du trajet d'alimentation en huile (15) se trouve à un emplacement, sur la surface d'appui (8a), qui est circonférentiellement vers l'extérieur dans une plage d'action de pression (R) où la pression provenant du tourillon de crosse (7) agit avec la plus grande force. La rainure d'alimentation en huile (16) n'est pas formée dans une telle plage d'action de pression (R).
PCT/JP2015/077605 2015-03-31 2015-09-29 Bielle et moteur du type à crosse comportant cette dernière WO2016157575A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580077620.8A CN107407323B (zh) 2015-03-31 2015-09-29 连接棒以及包括该连接棒的十字头型发动机
KR1020177023819A KR101957622B1 (ko) 2015-03-31 2015-09-29 연접봉 및 이것을 구비한 크로스헤드형 엔진

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JP2015-073316 2015-03-31
JP2015073316A JP6727758B2 (ja) 2015-03-31 2015-03-31 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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WO2016157575A1 true WO2016157575A1 (fr) 2016-10-06

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KR (1) KR101957622B1 (fr)
CN (1) CN107407323B (fr)
WO (1) WO2016157575A1 (fr)

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US11034116B2 (en) * 2017-08-04 2021-06-15 Aida Engineering, Ltd. Servo press machine
WO2023247817A1 (fr) * 2022-06-22 2023-12-28 Wärtsilä Finland Oy Coquille de palier, palier, moteur à piston et utilisation d'une coquille de palier

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JP7127293B2 (ja) * 2018-02-15 2022-08-30 トヨタ自動車株式会社 コネクティングロッド
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CN107407323B (zh) 2020-06-09
JP2016191463A (ja) 2016-11-10

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