EP2131031A1 - Motor - Google Patents

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Publication number
EP2131031A1
EP2131031A1 EP08722159A EP08722159A EP2131031A1 EP 2131031 A1 EP2131031 A1 EP 2131031A1 EP 08722159 A EP08722159 A EP 08722159A EP 08722159 A EP08722159 A EP 08722159A EP 2131031 A1 EP2131031 A1 EP 2131031A1
Authority
EP
European Patent Office
Prior art keywords
wall
cylinder body
cylinder
engine according
cylinder bore
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.)
Granted
Application number
EP08722159A
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English (en)
French (fr)
Other versions
EP2131031A4 (de
EP2131031B1 (de
Inventor
Yutaka Mine
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.)
Yamaha Motor Co Ltd
Original Assignee
Yamaha Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yamaha Motor Co Ltd filed Critical Yamaha Motor Co Ltd
Publication of EP2131031A1 publication Critical patent/EP2131031A1/de
Publication of EP2131031A4 publication Critical patent/EP2131031A4/de
Application granted granted Critical
Publication of EP2131031B1 publication Critical patent/EP2131031B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/0002—Cylinder arrangements
    • F02F7/0004—Crankcases of one-cylinder engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/02—Cylinders; Cylinder heads  having cooling means
    • F02F1/10—Cylinders; Cylinder heads  having cooling means for liquid cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/02—Cylinders; Cylinder heads  having cooling means
    • F02F1/10—Cylinders; Cylinder heads  having cooling means for liquid cooling
    • F02F1/14—Cylinders with means for directing, guiding or distributing liquid stream
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/02—Attachment or mounting of cylinder heads on cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/006—Camshaft or pushrod housings
    • F02F2007/0063—Head bolts; Arrangements of cylinder head bolts

Definitions

  • the present invention relates to an engine.
  • a water-cooled engine among engines of motorcycles is formed with a water jacket between a cylinder bore wall and a cylinder body outer wall, and circulates cooling water between an interior of the jacket and a radiator.
  • a through bolt which is made to pass through along an axial direction
  • the aforementioned water-cooled engine is provided with a bolt through-hole in a cylinder body outer wall.
  • a request for downsizing an engine is highly intensive because a mounting space for the engine is extremely limited.
  • a cylinder body cannot be simply enlarged as a whole.
  • the cylinder bore wall is enlarged, it directly affects forming positions of bolt through-holes in a cylinder body outer wall side.
  • the bolt through-holes are disposed in a plurality of places around the cylinder bore wall, and if these holes step back outward at once along with the enlargement of the cylinder bore wall, both the cylinder body and a cylinder head will grow in size. Due to such circumstances, it has been conventionally difficult to easily response to the request for downsizing the engine.
  • the invention is made in view of the above circumstance and aims to accomplish downsizing of an engine.
  • the invention has a structure including: a cylinder body having a cylinder bore wall, whose inner peripheral surface is formed in a circular shape, for accommodating a piston to be slidable, a cylinder body outer wall disposed so as to surround the whole circumference of the cylinder bore wall and formed with a bolt through-hole along an axial direction, and a coolant storing groove between the cylinder bore wall and the cylinder body outer wall; a cylinder head mounted on one end of the cylinder body in the axial direction and formed with a bolt hole coaxially connected to the bolt through-hole in the cylinder body side; a through bolt inserted in the bolt hole and the bolt through-hole for securing and tightening the cylinder body and the cylinder head; a projection formed such that a part of a wall around the bolt through-hole on the cylinder body outer wall projects to the coolant storing groove along the axial direction; and a thin wall portion disposed in a portion on the cylinder bore wall, which faces the projection in
  • An example of a preferred configuration is characterized that a part of the projection that bulges out the most into the coolant storing groove and a thinnest part of the thin wall portion face each other in the radial direction of the cylinder body.
  • Another example of the preferred configuration is characterized that the thin wall portion and the projection are formed throughout the entire depth of the coolant storing groove.
  • Another example of the preferred configuration is characterized that the thin wall portion is formed nearly in the same width as the projection.
  • a surface of the thin wall portion that faces the projection is a flat surface.
  • the thin wall portion has the flat surface irrespective of a contour shape of the projection.
  • Another example of the preferred configuration is characterized that the whole circumference of the coolant storing groove is formed to be open toward the cylinder head side.
  • the entire cylinder body can be formed by forming dies in a simple structure that open and close along an opening direction of the coolant storing groove, it is possible to facilitate manufacture of the engine.
  • Another example of the preferred configuration is characterized that plural places where the projection and the thin wall portion face each other in the radial direction are provided in a circumferential direction in the coolant storing groove.
  • the groove depth of the coolant storing groove is relatively shallow in at least one place, and the rest of the places in the coolant storing groove are formed relatively deep.
  • the groove depth of the coolant storing groove is not equal in the whole circumference. Among areas that correspond with the places where the projections are formed, some places are set shallower than the others. The reason is as follows.
  • the coolant storing groove is shaped, it is common to set a "draft" for dies cutting such that a bottom surface side of the coolant storing groove, that is, a tip side of forming dies is thin, and an open side of the groove, that is, a root side of the forming dies is thick.
  • a groove width (opening width) of the coolant storing groove may occasionally be slightly narrower in the place where the projection is formed than the other places even when the thin wall portion is set in the cylinder bore side.
  • the groove depth is made shallower in the place where the projection is formed and where the groove width is narrower than the other places; therefore, the tip of a die structure part that shapes the projection does not become too narrow. Consequently, it is possible to retain the strength of the forming dies for shaping the projection.
  • a hollow chain housing section for housing a cam chain capable of driving a camshaft is continuously provided in the cylinder body outer wall, that a portion of the cylinder body outer wall projects into the chain housing section to be a bulging part, and that the bulging part is disposed away from a track of the cam chain.
  • a part (bulging part) of the cylinder body outer wall is designed to cut in an interior of the chain housing section in which the chain housing section of the cam chain is continuously provided in the cylinder body outer wall.
  • an inlet of coolant is formed to be open into the coolant storing groove in the cylinder body outer wall and is disposed in an area where the groove depth of the coolant storing groove is relatively deep.
  • the coolant inlet is disposed in a portion where the groove depth is deep.
  • inflow resistance of the coolant from the coolant inlet becomes large; therefore, it may prevent smooth circulation movement of the coolant.
  • the inflow resistance of the coolant is little, and thus, it is possible to smoothly circulate the coolant.
  • At least the cylinder bore wall is made of aluminum alloy, and that the inner wall of the cylinder bore wall is formed with a hard layer whose hardness is higher than a base layer of the cylinder bore wall.
  • Another example of the preferred configuration is characterized that a liner made of aluminum alloy is provided on the inner surface of the cylinder bore wall and that the hard layer is formed on an inner surface of the liner.
  • the hard layer is a plating layer containing a silicon component. According to this configuration, it is possible to enhance the abrasion resistance of the surface that slidingly contacts the piston due to the plating layer containing the silicon component.
  • the hard layer is the plating layer containing a nickel component. According to this configuration, it is possible to enhance the abrasion resistance of the sliding contact surface with the piston due to the plating layer containing the nickel component.
  • the hard layer is a dispersed plating layer of Ni-P-SiC. According to this configuration, it is possible to enhance the abrasion resistance of the sliding contact surface with the piston due to the dispersed plating layer of Ni-P-SiC.
  • At least the cylinder bore wall is a vacuum die-casting piece made of aluminum alloy containing 13 to 22 wt% of silicon.
  • At least the cylinder bore wall is the vacuum die-casting piece made of aluminum alloy containing 18 to 22 wt% of silicon. This configuration enables to further enhance the abrasion resistance.
  • Another example of the preferred configuration is characterized that a silica crystal projects from the inner surface of the cylinder bore wall.
  • the silica crystal projected from the inner wall of the cylinder bore wall contacts the piston and forms the sliding contact surface, and lubricating oil can be spread over a surrounding portion of silica crystal that is relatively dented. Therefore, it is able to enhance the abrasion resistance.
  • FIG. 1 illustrates the configuration surrounding an engine of a motorcycle.
  • the engine is a water-cooled, four-stroke, one-cylinder engine and is configured by including a crankcase 2 for supporting a crankshaft 1 for rotation, a cylinder body 3 attached to the crankcase 2, and a cylinder head 4 attached to a front side of the cylinder body 3 in an axial direction.
  • crankcase 2 for supporting a crankshaft 1 for rotation
  • cylinder body 3 attached to the crankcase 2
  • a cylinder head 4 attached to a front side of the cylinder body 3 in an axial direction.
  • the crankshaft 1 is configured by including a symmetrical pair of crank webs 6, and a crank pin 7 for connecting the crank webs 6 with each other.
  • a piston 9 is connected to the crank pin 7 via a connecting rod 8.
  • an automatic gear change mechanism 10 of a V-belt winding type for driving a rear wheel is disposed to the left end of a vehicle body from the crankshaft 1.
  • a cam chain drive sprocket 11 is fitted between a coupling portion of the connecting rod 8 with the crankshaft 1 and the automatic gear change mechanism 10, and makes a camshaft 12 rotatable by a cam chain 14, which runs between the cam chain sprocket 11 and a cam chain driven sprocket 13 fitted to the camshaft 12.
  • a flywheel magneto 15 for power generation and a fan 16 are arranged in parallel with each other axially at a right end of the vehicle body from the crankshaft 1. Further, a radiator 17 for cooling off the engine with cooling water is disposed in a lateral side of the fan 16 and is covered with a cover from the side.
  • first cooling water tube 18 is connected to a lower tank side of the radiator 17, and the other end of the first cooling water tube 18 is connected to a suction side of a water pump 19, which drives in conjunction with the camshaft 12.
  • second cooling water tube 20 is connected to an upper tank side of the radiator 17, and the other end of the second cooling water tube 20 is connected to a water jacket 37 in the cylinder head 4.
  • a discharge side of the water pump 19 and a water jacket 21 in the cylinder body 3 side (hereinafter the water jacket 21 in the cylinder body 3 side will be simply referred to as the water jacket 21 unless otherwise noted) are connected by a third cooling water tube 22. Thereby, the cooling water can be circulated between the radiator 17 and the water jacket 21.
  • a valve operating device for driving a suction valve and an exhaust valve by the camshaft 12, a spark plug, and the like are integrated in the cylinder head 4.
  • plural bolt holes 23 for making the through bolt 5 pass through are formed along the axial direction.
  • Each of the bolt holes 23 fits together with corresponding one of bolt through-holes 24 provided in the same number as the bolt holes 23 in the cylinder body 3 and can be linked coaxially.
  • the bolt through-holes 24 are, as shown in FIG. 3 , disposed in approximately equally-spaced four places around a central axis of a cylinder bore wall 27. However, such an angle spacing is adjustable in accordance with a surrounding structure, and the holes need not be necessarily disposed equally-spaced.
  • Each of the bolt through-holes 24 can fit together with a screw hole 25 formed in a similar manner as the bolt through-hole 24 in the crankcase 2 side.
  • the through bolt 5, both ends of which are formed with screw parts 5A, is loosely inserted in the bolt holes 23, the bolt through-hole 24 and the screw hole 25, all of which coaxially fit together.
  • One screw part 5A is screwed in the screw hole 25 while the other screw part 5A projects from an exterior surface of the crankcase 2 and is tightened by a nut 26. Thereby, the cylinder head 4 and the cylinder body 3 are tightened and secured to the crankcase 2.
  • the cylinder body 3 is polymerized to a foreside of the crankcase 2 in a vehicle body direction, and in this embodiment, is formed in one by aluminum alloy.
  • the cylinder bore wall 27 for accommodating the piston 9 to be slidable is formed in an interior of the cylinder body 3.
  • the cylinder bore wall 27 is roughly formed in a cylindrical shape, and both ends thereof in the axial direction are concurrently formed to be open.
  • a cylinder body outer wall 28 is provided so as to coaxially surround the cylinder bore wall 27.
  • a chain housing section 29 for housing the cam chain 14 is continuously provided in a sidepiece of the cylinder body outer wall 28.
  • the chain housing section 29 is also formed hollow with both ends in the axial direction open, and both of the open ends respectively connect to a cam chain housing space 30 in the crankcase 2 side and the cylinder head 4 side.
  • the sidepiece of the cylinder body outer wall 28 is formed such that a part of the sidepiece (a bulging part 31) is cut into the chain housing section 29.
  • a bulging position of the bulging part 31 is set roughly in the center of the chain housing section 29, and thus, the intervention with the cam chain 14 is avoided.
  • the width measurement of the cylinder body 3 as a whole is to be downsized by the crossover.
  • the water jacket 21 (a coolant storing groove) is formed in a concentric ring shape around the whole circumference between the cylinder bore wall 27 and the cylinder body outer wall 28.
  • the aforementioned four bolt through-holes 24 are disposed equiangularly around the water jacket 21 in the cylinder body outer wall 28 (the angle spacing is adjustable accordingly, and the holes need not be spaced equiangularly).
  • each of the bolt through-holes 24 is disposed such that a portion of an area surrounding it projects in an arc shape into the water jacket 21, and forms projections 32A to 32D.
  • Each of the projections 32A to 32D is formed throughout the entire depth range of the water jacket 21.
  • the areas around the two bolt through-holes 24 located on the opposite side of the chain housing section 29 project in the arc shape in a planar view from the cylinder body outer wall 28 to the outside in the radial direction whereas the other two, which are disposed in the chain housing section 29 side, share the areas around the holes with the chain housing section 29.
  • the thin wall portions 33A to 33D are formed in portions of an exterior surface of the cylinder bore wall 27, which respectively face the projections 32A to 32D.
  • Each of the thin wall portions 33A to 33D is formed thinner in the radial direction than other portions of the cylinder bore wall 27 except the portions thereof that face each of the projections 32A to 32D.
  • Each of the thin wall portions 33A to 33D is formed with a flat surface in a predetermined width that extends along the axial direction, is formed throughout the entire depth range of the water jacket 21 as the projections 32A to 32D, and is formed nearly in the same width as the projections 32A to 32D.
  • the tips of the projections 32A to 32D that bulge out the most into the water jacket 21 and the centers of the respective thin wall portions 33A to 33D in the width direction, that is, the most dented parts on the exterior surface of the cylinder bore wall 27 against the water jacket 21, are in a positional relationship to face one another in the radial direction of the cylinder body 3.
  • the groove width of the water jacket 21 is formed slightly narrow in the area where each of the projections 32A to 32D faces corresponding one of the thin wall portions 33A to 33D compared to the area where these do not face each other except one place (the area where the projection 32B faces the thin wall portion 33B). Also, regarding the groove depth, as shown in FIG. 5 , the area where each of the projections 32A to 32D faces corresponding one of the thin portions 33A to 33D is formed shallow compared to the area where these parts do not face each other except one place (the area where the projection 32B faces the thin wall portion 33B).
  • a groove bottom shape of the water jacket 21 is set such that changes in the shape between a shallow portion and a deep portion of the groove depth are gradually made.
  • the reason why the groove depth in the water jacket 21 is uneven is as follows (see FIG. 6 and FIG. 7 ).
  • the water jacket 21 is formed by forming dies which are openable and closable in a direction following the axial direction, and at the time of forming, a formed pin 34, which is corresponds with the water jacket 21, projects from one of the dies.
  • the formed pin 34 is configured with a draft, which is designed to taper in size in relation to "drafting" upon post-shaping.
  • FIG. 6 shows a condition in which the deep portion in the groove depth of the water jacket 21 is shaped.
  • FIG. 7 shows a shaping condition relative to the shallow portion in the groove depth of the water jacket 21 (the areas where the projections 32A, 32C, 32D and the respective thin wall portions 33A, 33C, 33D face each other).
  • the reason why the groove width of one of the four places where the projections 32A to 32D face the respective thin portions 33A to 33D is wider than the others is because only the place, which corresponds to the projection 32B, has a room in a surrounding space of the cylinder body 3, and a need to push the position of the corresponding bolt through-hole 24 toward the cylinder bore wall 27 side is a little compared to the other bolt through-hole.
  • only a curvature radius of the periphery of the projection 32B is formed smaller than the other projections 32A, 32C, 32D. Therefore, depending on a surrounding situation of the cylinder body 3, the groove depth of the water jacket 21 may be formed shallow in all the places where the projections are formed.
  • an inlet pipe 35 to which the aforementioned third cooling water tube 22 is connected, is formed in one to project outwardly in the radial direction, and is made possible to inlet cooling water from an inlet 37 that opens in the water jacket 21.
  • the inlet pipe 35 is disposed in the area where the projections 32A to 32D face the respective thin wall portions 33A to 33D and close to the chain housing section 29. That is, the inlet pipe 35 is disposed in the area where the groove depth of the water jacket 21 is deep. Also, in this embodiment, as shown in FIG.
  • an inlet recess 36 is formed by denting the outer wall of the water jacket 21 outwardly in the predetermined width range in the place where the inlet pipe 35 is disposed. Thereby, cooling water is introduced to the portion of the water jacket 21 where the groove width is wide and the groove depth is deep.
  • the radiator 17 is disposed not in front but lateral to the vehicle body from the engine. Thereby, the vehicle length in the longitudinal direction is shortened. On the contrary, the vehicle width is widened by that extent; however, the radiator 17 is located posterior to a leg of a rider or in an unused space where the interference with the rider' s leg does not become a problem. Therefore, the interference caused by widening the vehicle width does not become a problem.
  • the front portion of the vehicle where the radiator 17 is disposed laterally has to avoid the interference with the leg, the width of this portion in the engine of the first embodiment is narrowed as much as possible.
  • the cylinder body 3 in the cylinder body 3, it is configured such that the portions (the projections 32A to 32D) where the areas around the bolt through-holes 24 project into the water jacket 21 are provided, and that the thin wall portions 33A to 33D are provided in the cylinder bore wall 27 side in order to make a dent in the places where the thin portions 33A to 33D face the projections 32A to 32D.
  • the adoption of such configuration it is possible to downsize the engine compared to the configuration that does not provide the projections 32A to 32D. Therefore, the interference with the rider's leg is surely avoided, and this configuration contributes to expansion of a space around the engine. This can be said, in other words, that it is possible to enlarge the cylinder bore wall 27 as far as the external form of the engine is the same, thus, to increase the engine capacity.
  • the effort is made to simplify manufacture of the engine.
  • the cylinder body 3 can be shaped by forming dies with a simple structure, which opens and closes in the axial direction.
  • the groove depth of the water jacket 21 is not equalized along all its circumference, but is made shallower in the areas where the projections 32A, 32C, 32D face the respective thin wall portions 33A, 33C, 33D, that is, where the groove width tends to be narrower than the other areas. Therefore, it is possible to retain the strength of the formed pin 34 for shaping the water jacket 21.
  • the thin wall portions 33A to 33D Although it can be considered to adopt a curvature shape, which suits the contour shapes of the projections 32A to 32D, it makes the shape of the forming dies complicated.
  • the thin portions 33A to 33D are formed with flat surfaces. As a result, the shape of the forming dies is kept simple.
  • this embodiment further brings the following effect. That is, because the inlet pipe 35 for introducing cooling water into the water jacket 21 is disposed in the deep portion in the groove depth of the water jacket 21, and also because the groove width of the water jacket 21 is widened by forming the inlet recess 36 in the place where the inlet pipe 35 is disposed, the introduction of cooling water into the water jacket 21 is made smoothly.
  • Each of the second to the fourth embodiments shows structural ingenuity for improvement of abrasion resistance of a sliding contact surface on a cylinder body 103, which is made of aluminum alloy, with a piston.
  • the second and the third embodiments include a cylinder bore wall made with a hard layer.
  • a cylinder liner 140 formed in a cylindrical shape is formed by molding on an inner surface of a cylinder bore wall 127.
  • a cylinder liner 140 is made of aluminum alloy in generally the same composition as a cylinder body 103.
  • a hard layer that is harder (Rockwell hardness) than the cylinder bore wall 127 is formed on an inner surface (sliding contact surface with the piston) of the cylinder liner 140. This hard layer is formed by a plating film (plating layer).
  • An alumite film is formed on a surface of the cylinder liner 140 as a base processing prior to a plating treatment. Then, a dispersed plating treatment of Ni-P-SiC is applied, followed by honing.
  • coefficient of thermal expansion of the cylinder liner 140 is set 10% or over 10% smaller than that of the cylinder body 103, and a tightening force of the cylinder body 103 with respect to the cylinder liner 140 is not relaxed by solidification contraction or heat contraction after the solidification. Therefore, a gap is not produced between the cylinder liner 104 and the cylinder bore wall 127. This contributes to securement of high thermal conductivity of the cylinder body 103.
  • the plating layer is formed on the cylinder liner; however, in this embodiment, the cylinder liner is not used, but the hard layer is formed directly on the inner surface of the cylinder bore wall. More specifically, the plating layer that is harder than a base layer (base material portion) is formed on an inner surface layer of the cylinder bore wall. That is, the inner surface (the area which slidingly contacts the piston) of the cylinder bore wall is plated in a fast plating method (a method in which a plating solution is poured into the cylinder bore at high speed for electroplating). Thereby, the plating layer of either Ni-P-SiC or Ni-SiC is formed on the inner surface of the cylinder bore wall.
  • a fast plating method a method in which a plating solution is poured into the cylinder bore at high speed for electroplating.
  • the honing in which plane roughness is, for example, equal to or less than 1. 0 ⁇ mRz is applied to the surface of the plating layer. If the plane roughness is small as such, it is concerned that a retaining function of lubricating oil on the surface of the plating layer decreases and that seizing resistance decreases.
  • a deposited layer of TiN and the like may be formed on a surface of a piston ring.
  • the improvement of the abrasion resistance is achieved without the integration of a sleeve and the like into the cylinder bore wall. Therefore, it can contribute to downsizing of the cylinder bore wall, and consequently to further downsizing of the cylinder body.
  • the plating layer is described as the hard layer.
  • the plating layer one made of nickel plating or chrome plating can also be adopted.
  • a method by thermal spraying such as wire explosion spraying and plasma spraying is also possible, and is included in the invention.
  • the abrasion resistance to the piston is enhanced by causing a silica crystal to project from the inner surface of the cylinder bore wall without the plating treatment thereon.
  • the cylinder body in this embodiment is formed by aluminum alloy containing 73.4 wt% to 79. 6 wt% of aluminum, 13 wt% to 22 wt%, preferably, 18 wt% to 22 wt% of silicon, and 2.0 wt% to 3.0 wt% of copper.
  • the cylinder body obtained in the above method includes plural primary crystal silicon grains that make up the sliding surface that contacts the piston, and plural eutectic crystal silicon grains positioned between the plural primary crystal silicon grains.
  • the average grain radius of the plural primary crystal silicon grains is between 12 ⁇ m and 50 ⁇ m, and that of the plural eutectic crystal silicon grains is equal to or less than 7.5 ⁇ m.
  • the Rockwell hardness (HRB) of the sliding surface is between 60 and 80.
  • the third embodiment it is possible to enhance the abrasion resistance without use of the cylinder liner; therefore, it can contribute to downsizing of the cylinder bore wall, and consequently to further downsizing of the cylinder body. Also, because the silicon crystalline particles arise and project from the inner surface of the cylinder bore wall, these arising crystal silicon grains come in contact with the piston to form the sliding contact surfaces, and can spread lubricating oil throughout dented aluminum base surface surrounding the sliding contact surfaces. Therefore, it is also possible to enhance the abrasion resistance from this point of view.
  • an iron sleeve may be used instead of the above embodiments.
  • the iron sleeve is positioned in a predetermined position within the forming dies that form the cylinder body, and is cast along with forming. Accordingly, it is possible to obtain the cylinder body with which the iron sleeve is integrated, and the whole circumference of the iron sleeve is in close contact with the inner surface of the cylinder bore wall.
  • each of the thin wall portions 33A to 33D is formed with a flat surface, but it can be formed with a shape of circular arc and recession, which corresponds with the shape of the respective thin wall portions 33A to 33D.
  • crankcase can be formed in one with the cylinder body.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP08722159.4A 2007-04-05 2008-03-14 Motor Active EP2131031B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007099000A JP2010156202A (ja) 2007-04-05 2007-04-05 エンジン
PCT/JP2008/054763 WO2008126637A1 (ja) 2007-04-05 2008-03-14 エンジン

Publications (3)

Publication Number Publication Date
EP2131031A1 true EP2131031A1 (de) 2009-12-09
EP2131031A4 EP2131031A4 (de) 2013-01-02
EP2131031B1 EP2131031B1 (de) 2017-12-20

Family

ID=39863761

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08722159.4A Active EP2131031B1 (de) 2007-04-05 2008-03-14 Motor

Country Status (6)

Country Link
EP (1) EP2131031B1 (de)
JP (1) JP2010156202A (de)
CN (1) CN101652554B (de)
BR (1) BRPI0809489B1 (de)
TW (1) TWI328642B (de)
WO (1) WO2008126637A1 (de)

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EP2860381A1 (de) * 2013-06-28 2015-04-15 Yamaha Hatsudoki Kabushiki Kaisha Motor
US20150330328A1 (en) * 2012-12-21 2015-11-19 Caterpillar Motoren Gmbh & Co. Kg Cylinder head and engine block configuration
DE102015006930A1 (de) * 2015-05-28 2016-12-01 Volkswagen Aktiengesellschaft Brennkraftmaschine
EP3842629A1 (de) * 2019-12-24 2021-06-30 Yamaha Hatsudoki Kabushiki Kaisha Verbrennungsmotor, grätschsitzfahrzeug und verfahren zur herstellung eines verbrennungsmotors

Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
JP6057667B2 (ja) * 2012-10-30 2017-01-11 ダイハツ工業株式会社 内燃機関のシリンダブロック
JP7135560B2 (ja) * 2018-08-08 2022-09-13 スズキ株式会社 エンジンの組み付け構造及び車両
JP7274916B2 (ja) * 2019-04-03 2023-05-17 ナブテスコ株式会社 ポンプユニット及び建設機械

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DE4244502C1 (de) * 1992-12-30 1994-03-17 Bruehl Aluminiumtechnik Zylinderkurbelgehäuse und Verfahren zu seiner Herstellung
EP0690250A1 (de) * 1994-06-30 1996-01-03 Yamaha Hatsudoki Kabushiki Kaisha Zylinder-Einheit und Verfahren zum Herstellen von Laufflächen
EP0719917A1 (de) * 1994-12-26 1996-07-03 Yamaha Hatsudoki Kabushiki Kaisha Zylindereinheit und Verfahren zur Formung ihrer Gleitfläche
DE19523484A1 (de) * 1995-06-28 1997-01-02 Daimler Benz Ag Zylinderlaufbüchse aus einer übereutektischen Aluminium/Silizium-Legierung zum Eingießen in ein Kurbelgehäuse einer Hubkolbenmaschine und Verfahren zur Herstellung einer solchen Zylinderlaufbüchse
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US20150330328A1 (en) * 2012-12-21 2015-11-19 Caterpillar Motoren Gmbh & Co. Kg Cylinder head and engine block configuration
US10082100B2 (en) * 2012-12-21 2018-09-25 Caterpillar Motoren Gmbh & Co. Kg Cylinder head and engine block configuration
EP2860381A1 (de) * 2013-06-28 2015-04-15 Yamaha Hatsudoki Kabushiki Kaisha Motor
EP3130778A1 (de) * 2013-06-28 2017-02-15 Yamaha Hatsudoki Kabushiki Kaisha Motor
DE102015006930A1 (de) * 2015-05-28 2016-12-01 Volkswagen Aktiengesellschaft Brennkraftmaschine
EP3842629A1 (de) * 2019-12-24 2021-06-30 Yamaha Hatsudoki Kabushiki Kaisha Verbrennungsmotor, grätschsitzfahrzeug und verfahren zur herstellung eines verbrennungsmotors

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TW200914721A (en) 2009-04-01
CN101652554A (zh) 2010-02-17
EP2131031A4 (de) 2013-01-02
CN101652554B (zh) 2012-07-04
BRPI0809489B1 (pt) 2019-08-13
EP2131031B1 (de) 2017-12-20
BRPI0809489A2 (pt) 2014-09-09
JP2010156202A (ja) 2010-07-15
WO2008126637A1 (ja) 2008-10-23
TWI328642B (en) 2010-08-11

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