EP2131031B1 - Engine - Google Patents
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- Publication number
- EP2131031B1 EP2131031B1 EP08722159.4A EP08722159A EP2131031B1 EP 2131031 B1 EP2131031 B1 EP 2131031B1 EP 08722159 A EP08722159 A EP 08722159A EP 2131031 B1 EP2131031 B1 EP 2131031B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- wall
- cylinder
- cylinder body
- engine according
- bolt
- 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.)
- Active
Links
- 239000002826 coolant Substances 0.000 claims description 40
- 238000007747 plating Methods 0.000 claims description 27
- XUIMIQQOPSSXEZ-UHFFFAOYSA-N Silicon Chemical compound [Si] XUIMIQQOPSSXEZ-UHFFFAOYSA-N 0.000 claims description 18
- 229910052710 silicon Inorganic materials 0.000 claims description 18
- 239000010703 silicon Substances 0.000 claims description 18
- 229910000838 Al alloy Inorganic materials 0.000 claims description 14
- 239000013078 crystal Substances 0.000 claims description 11
- PXHVJJICTQNCMI-UHFFFAOYSA-N Nickel Chemical compound [Ni] PXHVJJICTQNCMI-UHFFFAOYSA-N 0.000 claims description 8
- 238000004512 die casting Methods 0.000 claims description 6
- 229910052759 nickel Inorganic materials 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 claims description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 40
- 239000010410 layer Substances 0.000 description 29
- 238000005299 abrasion Methods 0.000 description 14
- 239000000498 cooling water Substances 0.000 description 13
- 238000007493 shaping process Methods 0.000 description 11
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 8
- VYPSYNLAJGMNEJ-UHFFFAOYSA-N Silicium dioxide Chemical compound O=[Si]=O VYPSYNLAJGMNEJ-UHFFFAOYSA-N 0.000 description 8
- 238000005259 measurement Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 6
- 229910052742 iron Inorganic materials 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 239000000377 silicon dioxide Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000008602 contraction Effects 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000005496 eutectics Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 238000007711 solidification Methods 0.000 description 2
- 230000008023 solidification Effects 0.000 description 2
- VYZAMTAEIAYCRO-UHFFFAOYSA-N Chromium Chemical compound [Cr] VYZAMTAEIAYCRO-UHFFFAOYSA-N 0.000 description 1
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 229910002650 Ni-SiC Inorganic materials 0.000 description 1
- ATJFFYVFTNAWJD-UHFFFAOYSA-N Tin Chemical compound [Sn] ATJFFYVFTNAWJD-UHFFFAOYSA-N 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000009713 electroplating Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000007750 plasma spraying Methods 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 239000002344 surface layer Substances 0.000 description 1
- 238000007751 thermal spraying Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
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.
- JP 2006-144559 A An example of such an engine is disclosed in JP 2006-144559 A .
- JP 2006-138226 A describes an internal combustion engine with reduced size, weight and cost by division of a cylinder block and improved roundness of a cylinder bore and strength of the cylinder block.
- the cylinder block is divided to a cylinder and a crankcase, a first fastening bolt passes through a bearing cap and the crankcase from a lower part and a second fastening bolt passes through a cylinder head and the cylinder. Threaded engagement at tip part of each fastening bolt fastens the cylinder head, the cylinder block and the bearing cap.
- 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 cylinder head 4 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.
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Description
- The present invention relates to an engine.
- Conventionally, 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. Generally, there are many engines with a structure in which a cylinder body and a cylinder head are secured and tightened by a through bolt, which is made to pass through along an axial direction, and the aforementioned water-cooled engine is provided with a bolt through-hole in a cylinder body outer wall. An example of such an engine is disclosed in
JP 2006-144559 A -
JP 2006-138226 A - Now, in a case of a motorcycle, a request for downsizing an engine is highly intensive because a mounting space for the engine is extremely limited. Thus, even if engine displacement is increased, that is, even if an inside diameter of a cylinder bore wall becomes larger, a cylinder body cannot be simply enlarged as a whole. For example, if 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.
- This is achieved by an engine as defined in the independent claim.
- In order to accomplish the object above, 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 a radial direction and formed thinner in a radial direction than a portion of the cylinder bore wall that does not face the projection.
- According to this structure, even if a portion of the wall around the bolt through-hole projects to the coolant storing groove, it is unnecessary to move the position where the bolt through-hole is provided outwardly along with enlargement of a bore diameter (inside diameter of the cylinder bore wall). It is because the thin wall portion is formed in a facing position in the cylinder bore wall side. Therefore, it is possible to downsize the engine. Conversely, the engine displacement can be increased while the engine size (external form) is retained as is.
- 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.
- According to this configuration, because of a positional relationship that the part of the projection that projects the most and the thinnest part of the thin wall portion face each other in the radial direction, it is possible to effectively avoid a bulge of the projection.
- 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.
- According to this configuration, because the projection and the thin wall portion face each other throughout an entire depth range of the coolant storing groove, it is possible to effectively avoid the bulge of the projection in a depth direction 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.
- According to this configuration, it is possible to effectively avoid the bulge of the projection in a width direction.
- Another example of the preferred configuration is characterized that a surface of the thin wall portion that faces the projection is a flat surface.
- According to this configuration, it is possible to simplify a mold shape because 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.
- According to this configuration, because 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.
- In this configuration, 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. When 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. On the other hand, 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. In such a case, if the groove depth is made equal for the whole circumference, the lack of strength becomes a concern at the tip of the forming dies, which becomes sharper in the place where the projection is formed in relation to drafting and the groove width is narrow than the other places.
- However, according to the above structure, 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.
- Another example of the preferred configuration is characterized that 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.
- According to this configuration, 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. Thereby, it is effective for downsizing the engine because the chain housing section is positioned to overlap with the cylinder body outer wall in an aligned direction.
- Another example of the preferred configuration is characterized that 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.
- According to this configuration, the coolant inlet is disposed in a portion where the groove depth is deep. On the contrary, if the coolant inlet is disposed in a shallow portion of the groove depth, inflow resistance of the coolant from the coolant inlet becomes large; therefore, it may prevent smooth circulation movement of the coolant. However, with placement as described above, the inflow resistance of the coolant is little, and thus, it is possible to smoothly circulate the coolant.
- Another example of the preferred configuration is characterized that 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.
- According to this configuration, it is possible to enhance abrasion resistance of a sliding contact surface on the cylinder bore wall with a piston.
- 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.
- Also, with this configuration, it is possible to enhance the abrasion resistance of the sliding contact surface with the piston.
- Another example of the preferred configuration is characterized that 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.
- Another example of the preferred configuration is characterized that 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.
- Another example of the preferred configuration is characterized that 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.
- Another example of the preferred configuration is characterized that at least the cylinder bore wall is a vacuum die-casting piece made of aluminum alloy containing 13 to 22 wt% of silicon.
- According to this configuration, it is possible to enhance the abrasion resistance of the sliding contact surface on the cylinder bore wall without forming the plating layer.
- Another example of the further preferred configuration is characterized that 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.
- According to this configuration, 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.
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Fig. 1 is a cross-sectional view of an engine. -
Fig. 2 is a cross-sectional view of a place where a through bolt appears. -
Fig. 3 is a plain view of a cylinder body by itself. -
FIG. 4 is a cross-sectional view taken along the line IV-IV inFIG. 3 . -
FIG. 5 is a cross-sectional view taken along the line V-V inFIG. 3 . -
Fig. 6 is a cross-sectional view showing a shaping condition with respect to a deep portion of a water jacket. -
Fig. 7 is a cross-sectional view showing the shaping condition with respect to a shallow portion of the water jacket. -
FIG. 8 is an enlarged cross-sectional view of a cylinder liner portion according to the second embodiment. -
- 3: cylinder body
- 4: cylinder head
- 5: through bolt
- 21: water jacket (coolant storing groove)
- 24: bolt through-hole
- 27: cylinder bore wall
- 29: chain housing section
- 32A-32D: projection
- 33A-33D: thin wall portion
- 34: formed pin
- 35: inlet pipe
- A first to a fourth embodiments according to the invention will be hereinafter described.
- A description is made of the first embodiment of the invention with reference to
FIG.1 to FIG.7 .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 acrankcase 2 for supporting a crankshaft 1 for rotation, acylinder body 3 attached to thecrankcase 2, and acylinder head 4 attached to a front side of thecylinder body 3 in an axial direction. These three components are tightened and secured by a throughbolt 5, which will be described later. - The crankshaft 1 is configured by including a symmetrical pair of crank
webs 6, and a crankpin 7 for connecting thecrank webs 6 with each other. Apiston 9 is connected to the crankpin 7 via a connectingrod 8. Also, 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. In addition, a cam chain drive sprocket 11 is fitted between a coupling portion of the connectingrod 8 with the crankshaft 1 and the automatic gear change mechanism 10, and makes acamshaft 12 rotatable by acam chain 14, which runs between the cam chain sprocket 11 and a cam chain drivensprocket 13 fitted to thecamshaft 12. - Meanwhile, a
flywheel magneto 15 for power generation and afan 16 are arranged in parallel with each other axially at a right end of the vehicle body from the crankshaft 1. Further, aradiator 17 for cooling off the engine with cooling water is disposed in a lateral side of thefan 16 and is covered with a cover from the side. - One end of a first
cooling water tube 18 is connected to a lower tank side of theradiator 17, and the other end of the firstcooling water tube 18 is connected to a suction side of awater pump 19, which drives in conjunction with thecamshaft 12. Also, one end of a secondcooling water tube 20 is connected to an upper tank side of theradiator 17, and the other end of the secondcooling water tube 20 is connected to awater jacket 37 in thecylinder head 4. Furthermore, a discharge side of thewater pump 19 and awater jacket 21 in thecylinder body 3 side (hereinafter thewater jacket 21 in thecylinder body 3 side will be simply referred to as thewater jacket 21 unless otherwise noted) are connected by a thirdcooling water tube 22. Thereby, the cooling water can be circulated between theradiator 17 and thewater 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 thecylinder head 4. In addition, in thecylinder head 4, plural bolt holes 23 for making the throughbolt 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 thecylinder body 3 and can be linked coaxially. The bolt through-holes 24 are, as shown inFIG. 3 , disposed in approximately equally-spaced four places around a central axis of acylinder 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 ascrew hole 25 formed in a similar manner as the bolt through-hole 24 in thecrankcase 2 side. The throughbolt 5, both ends of which are formed withscrew parts 5A, is loosely inserted in the bolt holes 23, the bolt through-hole 24 and thescrew hole 25, all of which coaxially fit together. Onescrew part 5A is screwed in thescrew hole 25 while theother screw part 5A projects from an exterior surface of thecylinder head 4 and is tightened by anut 26. Thereby, thecylinder head 4 and thecylinder body 3 are tightened and secured to thecrankcase 2. - The
cylinder body 3 is polymerized to a foreside of thecrankcase 2 in a vehicle body direction, and in this embodiment, is formed in one by aluminum alloy. As shown inFIG. 3 , the cylinder borewall 27 for accommodating thepiston 9 to be slidable is formed in an interior of thecylinder body 3. The cylinder borewall 27 is roughly formed in a cylindrical shape, and both ends thereof in the axial direction are concurrently formed to be open. On the periphery of the cylinder borewall 27, a cylinder bodyouter wall 28 is provided so as to coaxially surround the cylinder borewall 27. Achain housing section 29 for housing thecam chain 14 is continuously provided in a sidepiece of the cylinder bodyouter wall 28. Thechain 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 camchain housing space 30 in thecrankcase 2 side and thecylinder head 4 side. - Also, as shown in
FIG. 3 , the sidepiece of the cylinder bodyouter wall 28 is formed such that a part of the sidepiece (a bulging part 31) is cut into thechain housing section 29. A bulging position of the bulgingpart 31 is set roughly in the center of thechain housing section 29, and thus, the intervention with thecam chain 14 is avoided. In this way, because a part (the bulging part 31) of the cylinder bodyouter wall 28 is disposed so as to overlap with thechain housing section 29 in an aligned direction of these, the width measurement of thecylinder body 3 as a whole is to be downsized by the crossover. - In addition, in the
cylinder body 3, the water jacket 21 (a coolant storing groove) is formed in a concentric ring shape around the whole circumference between the cylinder borewall 27 and the cylinder bodyouter wall 28. Further, the aforementioned four bolt through-holes 24 are disposed equiangularly around thewater jacket 21 in the cylinder body outer wall 28 (the angle spacing is adjustable accordingly, and the holes need not be spaced equiangularly). Furthermore, each of the bolt through-holes 24 is disposed such that a portion of an area surrounding it projects in an arc shape into thewater jacket 21, and formsprojections 32A to 32D. Each of theprojections 32A to 32D is formed throughout the entire depth range of thewater jacket 21. Meanwhile, the areas around the two bolt through-holes 24 located on the opposite side of thechain housing section 29 project in the arc shape in a planar view from the cylinder bodyouter wall 28 to the outside in the radial direction whereas the other two, which are disposed in thechain housing section 29 side, share the areas around the holes with thechain housing section 29. - On the other hand, the
thin wall portions 33A to 33D are formed in portions of an exterior surface of the cylinder borewall 27, which respectively face theprojections 32A to 32D. Each of thethin wall portions 33A to 33D is formed thinner in the radial direction than other portions of the cylinder borewall 27 except the portions thereof that face each of theprojections 32A to 32D. Each of thethin 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 thewater jacket 21 as theprojections 32A to 32D, and is formed nearly in the same width as theprojections 32A to 32D. In addition, as shown inFIG. 3 , the tips of theprojections 32A to 32D that bulge out the most into thewater jacket 21 and the centers of the respectivethin wall portions 33A to 33D in the width direction, that is, the most dented parts on the exterior surface of the cylinder borewall 27 against thewater jacket 21, are in a positional relationship to face one another in the radial direction of thecylinder body 3. - The groove width of the
water jacket 21 is formed slightly narrow in the area where each of theprojections 32A to 32D faces corresponding one of thethin wall portions 33A to 33D compared to the area where these do not face each other except one place (the area where theprojection 32B faces thethin wall portion 33B) . Also, regarding the groove depth, as shown inFIG. 5 , the area where each of theprojections 32A to 32D faces corresponding one of thethin 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 theprojection 32B faces thethin wall portion 33B). That is, the place where the groove width is either equal to or narrower than a fixed value among the area where each of the projections faces a corresponding one of the thin portions is formed shallow in comparison with the other areas (H1>H2, seeFIG.4 andFIG.5 ). Though not shown in detail, a groove bottom shape of thewater 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 (seeFIG. 6 andFIG. 7 ). Thewater 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 formedpin 34, which is corresponds with thewater jacket 21, projects from one of the dies. The formedpin 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 thewater jacket 21 is shaped. In a shaping portion of the area described above in the formedpin 34 for shaping thewater jacket 21, the thickness measurement of the elementary portion is W1, and the draft configured on the formed pin 34 (an angle made by a line drawn parallel to the central axis of the formedpin 34 and a generatrix of the periphery of the formed pin 34) isθ1. On the other hand,FIG. 7 shows a shaping condition relative to the shallow portion in the groove depth of the water jacket 21 (the areas where theprojections thin wall portions pin 34 for shaping the areas, the thickness measurement of the elementary portion is set to be thin as W2 (W1>W2); however, it is configured to be roughly equal in terms of the draftθ2 (θ1=θ2). Therefore, the whole circumference of the formedpin 34 is configured to be roughly equal regarding the draft; however, the thickness measurement and the length measurement are varied between the areas where theprojections thin portions projections thin portions pin 34 is locally weakened. Consequently, in this embodiment, the strength of the formedpin 34 is to be retained by shortening the measurement of the portions for shaping the areas where theprojections thin portions - By the way, the reason why the groove width of one of the four places where the
projections 32A to 32D face the respectivethin portions 33A to 33D is wider than the others is because only the place, which corresponds to theprojection 32B, has a room in a surrounding space of thecylinder body 3, and a need to push the position of the corresponding bolt through-hole 24 toward the cylinder borewall 27 side is a little compared to the other bolt through-hole. Thus, only a curvature radius of the periphery of theprojection 32B is formed smaller than theother projections cylinder body 3, the groove depth of thewater jacket 21 may be formed shallow in all the places where the projections are formed. - In addition, on the cylinder body
outer wall 28, aninlet pipe 35, to which the aforementioned thirdcooling 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 aninlet 37 that opens in thewater jacket 21. In more detail, theinlet pipe 35 is disposed in the area where theprojections 32A to 32D face the respectivethin wall portions 33A to 33D and close to thechain housing section 29. That is, theinlet pipe 35 is disposed in the area where the groove depth of thewater jacket 21 is deep. Also, in this embodiment, as shown inFIG. 3 , an inlet recess 36 is formed by denting the outer wall of thewater jacket 21 outwardly in the predetermined width range in the place where theinlet pipe 35 is disposed. Thereby, cooling water is introduced to the portion of thewater jacket 21 where the groove width is wide and the groove depth is deep. - Next, the operating effects of the first embodiment that is configured as described above is specifically described. As mentioned before, in this embodiment, 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, theradiator 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. Although the front portion of the vehicle where theradiator 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. - That is, in this embodiment, in the
cylinder body 3, it is configured such that the portions (theprojections 32A to 32D) where the areas around the bolt through-holes 24 project into thewater jacket 21 are provided, and that thethin wall portions 33A to 33D are provided in the cylinder borewall 27 side in order to make a dent in the places where thethin portions 33A to 33D face theprojections 32A to 32D. By the adoption of such configuration, it is possible to downsize the engine compared to the configuration that does not provide theprojections 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 borewall 27 as far as the external form of the engine is the same, thus, to increase the engine capacity. - In addition, aligning the
chain housing section 29 and the cylinder bodyouter wall 28 to be overlapped with each other in the vehicle width direction, by cutting a portion of the cylinder bodyouter wall 28 into thechain housing section 29 for thecam chain 14, makes the above effect further effective. - Moreover, in the first embodiment, the effort is made to simplify manufacture of the engine. To begin with, because all the circumference of the
water jacket 21 is formed to be open in thecylinder head 4 side, thecylinder body 3 can be shaped by forming dies with a simple structure, which opens and closes in the axial direction. Further, the groove depth of thewater jacket 21 is not equalized along all its circumference, but is made shallower in the areas where theprojections thin wall portions pin 34 for shaping thewater jacket 21. Furthermore, upon forming thethin wall portions 33A to 33D, although it can be considered to adopt a curvature shape, which suits the contour shapes of theprojections 32A to 32D, it makes the shape of the forming dies complicated. Thus, in this embodiment, thethin portions 33A to 33D are formed with flat surfaces. As a result, the shape of the forming dies is kept simple. - In addition, this embodiment further brings the following effect. That is, because the
inlet pipe 35 for introducing cooling water into thewater jacket 21 is disposed in the deep portion in the groove depth of thewater jacket 21, and also because the groove width of thewater jacket 21 is widened by forming the inlet recess 36 in the place where theinlet pipe 35 is disposed, the introduction of cooling water into thewater 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. Among these embodiments, the second and the third embodiments include a cylinder bore wall made with a hard layer. - In the second embodiment, a
cylinder liner 140 formed in a cylindrical shape is formed by molding on an inner surface of acylinder bore wall 127. Acylinder liner 140 is made of aluminum alloy in generally the same composition as acylinder body 103. In addition, a hard layer that is harder (Rockwell hardness) than the cylinder borewall 127 is formed on an inner surface (sliding contact surface with the piston) of thecylinder 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. - In this embodiment, coefficient of thermal expansion of the
cylinder liner 140 is set 10% or over 10% smaller than that of thecylinder body 103, and a tightening force of thecylinder body 103 with respect to thecylinder 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 borewall 127. This contributes to securement of high thermal conductivity of thecylinder body 103. - In the second embodiment, 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. Then, the honing in which plane roughness is, for example, equal to or less than 1.0 µ 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. However, as a method to compensate for such problems, a deposited layer of TiN and the like may be formed on a surface of a piston ring.
- In the second embodiment configured as above, 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.
- In the aforementioned second and third embodiments, the plating layer is described as the hard layer. As the plating layer, one made of nickel plating or chrome plating can also be adopted. In addition, as a means of forming a hard layer in a method other than the plating processing, a method by thermal spraying such as wire explosion spraying and plasma spraying is also possible, and is included in the invention.
- In this embodiment, 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. In other words, 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.
- In general, because aluminum alloy with high content of silicon (equal to or over 9 wt%, especially equal to or over 16 wt%) is unsuitable for casting, the volume production by die-casting is considered to be difficult. However, according to a die-casting technology disclosed in
WO 2004/002658 pamphlet (submitted by the inventor of this application) and adopted in this embodiment, it is possible to effectively manufacture the cylinder body made of aluminum alloy containing silicon in such a large quantity. - 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 µm and 50 µm, and that of the plural eutectic crystal silicon grains is equal to or less than 7.5 µm. The Rockwell hardness (HRB) of the sliding surface is between 60 and 80.
- In this embodiment, as in 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.
- As a means to enhance the abrasion resistance of the sliding contact surface on the cylinder bore wall with the piston, an iron sleeve may be used instead of the above embodiments. In this case, 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.
- The invention is not limited to the embodiments described above with figures, and for example, the following embodiments are included in the technical scope of the invention. Further, various changes may be made without departing from the scope of the invention besides the embodiments described below.
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- (1)In this embodiment, the example in which the invention is adopted to a motorcycle is described; however, it is adoptable to an engine of a motorboat, snow mobile, and the like.
- (2) In this embodiment, it is described with water as a cooling medium, but it can be oil-based.
- (3) In this embodiment, each of the
thin wall portions 32A to 32D 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 respectivethin wall portions 33A to 33D. - (4)A cylinder body and a crankcase need not necessarily be formed separately, and the crankcase can be formed in one with the cylinder body.
Claims (17)
- An engine comprising:a cylinder body (3) having a cylinder bore wall (27), whose inner peripheral surface is in a circular shape, for accommodating a piston (9) to be slidable, a cylinder body outer wall (28) disposed so as to surround the whole circumference of the cylinder bore wall (27) and formed with a bolt through-hole (24) along an axial direction, and a coolant storing groove (21) between the cylinder bore wall (27) and the cylinder body outer wall (28);a cylinder head (4) mounted on one end of the cylinder body (3) in the axial direction, and formed with a bolt hole (23) coaxially connected with the bolt through-hole (24) of the cylinder body side;a bolt (5) inserted in the bolt hole (23) and the bolt through-hole (24) for securing and tightening the cylinder body (3) and the cylinder head (4);a projection (32A-32D) formed such that a part of a wall around the bolt through-hole (24) in the cylinder body outer wall (28) projects to the coolant storing groove (21) along the axial direction; anda thin wall portion (33A-33D) disposed in a portion of the cylinder bore wall (27) that faces the projection (32A-32D) in a radial direction and formed to be thinner than a portion of the cylinder bore wall (27) that does not face the projection (32A-32D),wherein the engine further comprises a crankcase (2) ;
characterized in that
the crankcase (2) has a screw hole (25); and
the through bolt (5), both ends of which are formed with screw parts (5A), is inserted in the bolt hole (23), the bolt through-hole (24) and the screw hole (25), all of which coaxially fit together, and one screw part (5A) is screwed in the screw hole (25) while the other screw part (5A) projects from an exterior surface of the cylinder head (4) and is tightened by a nut (26), thereby tightening and securing the cylinder head (4) and the cylinder body (3) to the crankcase (2). - The engine according to Claim 1, wherein
a part of the projection (32A-32D) that bulges out the most into the coolant storing groove (21) and a thinnest part of the thin wall portion (33A-33D) face each other in the radial direction of the cylinder body (3). - The engine according to Claim 1, wherein
the thin wall portion (33A-33D) and the projection (32A-32D) are formed throughout entire depth of the coolant storing groove (21). - The engine according to Claim 1, wherein
the thin wall portion (33A-33D) is formed nearly in the same width as the projection (32A-32D). - The engine according to Claim 1, wherein
a surface of the thin wall portion (33A-33D) that faces the projection (32A-32D) in the radial direction is a flat surface. - The engine according to Claim 1, wherein
the whole circumference of the coolant storing groove (21) is formed to be open toward the cylinder head side. - The engine according to Claim 1, wherein
plural places where the projection (32A-32D) and the thin wall portion (33A-33D) face each other in the radial direction are provided in a circumferential direction in the coolant storing groove (21),
groove depth of the coolant storing groove (21) is relatively shallow in at least one place, and
rest of the places in the coolant storing groove (21) are formed relatively deep. - The engine according to Claim 1, wherein
a hollow chain housing section (29) for housing a cam chain capable of driving a camshaft is continuously provided in the cylinder body outer wall (28),
a part of the cylinder body outer wall (28) projects into the chain housing section (29) to be a bulging part, and
the bulging part is disposed away from a track of the cam chain. - The engine according to Claim 7, wherein
an inlet of coolant is formed to be open into the coolant storing groove (21) in the cylinder body outer wall (28) and is disposed in an area where the groove depth of the coolant storing groove (21) is relatively deep. - The engine according to Claim 1, wherein
at least the cylinder bore wall (27) is made of aluminum alloy, and
an inner surface of the cylinder bore wall (27) is formed with a hard layer whose hardness is higher than a base layer of the cylinder bore wall (27). - The engine according to Claim 1, wherein
a liner (140) made of aluminum alloy is provided on the inner surface of the cylinder bore wall (27), and
the hard layer is formed on an inner surface of the liner (140). - The engine according to Claim 10 or 11, wherein
the hard layer is a plating layer containing a silicon component. - The engine according to Claim 10 or 11, wherein
the hard layer is a plating layer containing a nickel component. - The engine according to Claim 10 or 11, wherein
the hard layer is a dispersed plating layer of Ni-P-SiC. - The engine according to Claim 1, wherein
at least the cylinder bore wall (27) is a vacuum die-casting piece made of aluminum alloy containing 13 to 22 wt% of silicon. - The engine according to Claim 15, wherein
at least the cylinder bore wall (27) is the vacuum die-casting piece made of aluminum alloy containing 18 to 22 wt% of silicon. - The engine according to Claim 15 or 16, wherein
a silicon crystal projects from the inner surface of the cylinder bore wall (27).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007099000A JP2010156202A (en) | 2007-04-05 | 2007-04-05 | Engine |
PCT/JP2008/054763 WO2008126637A1 (en) | 2007-04-05 | 2008-03-14 | Engine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2131031A1 EP2131031A1 (en) | 2009-12-09 |
EP2131031A4 EP2131031A4 (en) | 2013-01-02 |
EP2131031B1 true EP2131031B1 (en) | 2017-12-20 |
Family
ID=39863761
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP08722159.4A Active EP2131031B1 (en) | 2007-04-05 | 2008-03-14 | Engine |
Country Status (6)
Country | Link |
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EP (1) | EP2131031B1 (en) |
JP (1) | JP2010156202A (en) |
CN (1) | CN101652554B (en) |
BR (1) | BRPI0809489B1 (en) |
TW (1) | TWI328642B (en) |
WO (1) | WO2008126637A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
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JP6057667B2 (en) * | 2012-10-30 | 2017-01-11 | ダイハツ工業株式会社 | Internal combustion engine cylinder block |
EP2746559B1 (en) * | 2012-12-21 | 2016-06-29 | Caterpillar Motoren GmbH & Co. KG | Cylinder head and engine block configuration |
JP6105410B2 (en) * | 2013-06-28 | 2017-03-29 | ヤマハ発動機株式会社 | engine |
DE102015006930A1 (en) * | 2015-05-28 | 2016-12-01 | Volkswagen Aktiengesellschaft | Internal combustion engine |
JP7135560B2 (en) * | 2018-08-08 | 2022-09-13 | スズキ株式会社 | Engine assembly structure and vehicle |
JP7274916B2 (en) * | 2019-04-03 | 2023-05-17 | ナブテスコ株式会社 | Pump units and construction machinery |
JP2021101109A (en) * | 2019-12-24 | 2021-07-08 | ヤマハ発動機株式会社 | Internal combustion engine, saddle-riding type vehicle and method for manufacturing internal combustion engine |
CN113915019B (en) * | 2021-11-03 | 2024-07-30 | 江门市大长江集团有限公司 | Cylinder head, cylinder body structure for engine and engine |
Family Cites Families (10)
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JP2662835B2 (en) * | 1991-10-25 | 1997-10-15 | 株式会社クボタ | Cylinder head fixing device to engine cylinder block |
DE4244502C1 (en) * | 1992-12-30 | 1994-03-17 | Bruehl Aluminiumtechnik | Cylinder crankcase and method for its manufacture |
JPH0821297A (en) * | 1994-06-30 | 1996-01-23 | Yamaha Motor Co Ltd | Slide contact part structure of internal combustion engine |
DE19523484C2 (en) * | 1995-06-28 | 2002-11-14 | Daimler Chrysler Ag | Method for producing a cylinder liner from a hypereutectic aluminum / silicon alloy for casting into a crankcase of a reciprocating piston machine and cylinder liner produced thereafter |
JP3483965B2 (en) * | 1994-12-26 | 2004-01-06 | ヤマハ発動機株式会社 | Sliding contact structure of internal combustion engine and molding method thereof |
GB9722449D0 (en) * | 1997-10-23 | 1997-12-24 | Ricardo Consulating Engineers | Engines of reciprocating piston type |
AU2003244075A1 (en) | 2002-06-26 | 2004-01-19 | Yamaha Hatsudoki Kabushiki Kaisha | Method and device for vacuum die casting of aluminum alloy, and aluminum alloy product |
JP4192845B2 (en) * | 2004-05-27 | 2008-12-10 | 三菱自動車工業株式会社 | Engine coolant passage structure |
JP2006138226A (en) * | 2004-11-10 | 2006-06-01 | Toyota Motor Corp | Internal combustion engine |
JP4382637B2 (en) * | 2004-11-16 | 2009-12-16 | ヤマハ発動機株式会社 | Cylinder block, engine, motor vehicle, and method of manufacturing cylinder block |
-
2007
- 2007-04-05 JP JP2007099000A patent/JP2010156202A/en active Pending
-
2008
- 2008-03-14 EP EP08722159.4A patent/EP2131031B1/en active Active
- 2008-03-14 CN CN2008800114946A patent/CN101652554B/en active Active
- 2008-03-14 BR BRPI0809489A patent/BRPI0809489B1/en active IP Right Grant
- 2008-03-14 WO PCT/JP2008/054763 patent/WO2008126637A1/en active Application Filing
- 2008-03-21 TW TW097109985A patent/TWI328642B/en active
Non-Patent Citations (1)
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Also Published As
Publication number | Publication date |
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BRPI0809489A2 (en) | 2014-09-09 |
TWI328642B (en) | 2010-08-11 |
EP2131031A1 (en) | 2009-12-09 |
JP2010156202A (en) | 2010-07-15 |
CN101652554A (en) | 2010-02-17 |
EP2131031A4 (en) | 2013-01-02 |
TW200914721A (en) | 2009-04-01 |
WO2008126637A1 (en) | 2008-10-23 |
BRPI0809489B1 (en) | 2019-08-13 |
CN101652554B (en) | 2012-07-04 |
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