JP2007120506A5 - - Google Patents

Description

Multi-cylinder engine

  The present invention relates to a multi-cylinder engine.

The present invention is based on the following technology.
As shown in FIG. 2, adjacent cylinder walls (1) and (1) are continuous to form a cylinder wall (2), and as shown in FIG. The direction of the cylinder head (4) is upward, the width direction of the cylinder block (6) is the left-right direction, and the installation direction of the crankshaft (5) is the front-rear direction.
Inter-cylinder bosses (7) and (7) are provided on the left and right sides of the upper part (2a) of the inter-cylinder wall (2), and these inter-cylinder bosses (7) and (7) are placed under the inter-cylinder wall (2). Continuing with the left and right sides of the offset part (2b)
Insert the head bolt (8) that penetrates the cylinder head (4) into the boss (7) between cylinders, and either or both of the boss (7) between cylinders and the lower part (2b) of the wall between cylinders (2). An upper female thread portion (9) is provided, and a head bolt (8) is screwed onto the upper female thread portion (9), and the cylinder head (4) is assembled to the cylinder block (6).
A bearing wall (10) of the crankshaft (5) is formed in the crankcase of the cylinder block (6), and the bearing wall (10) can be divided into an upper wall portion (10a) and a lower wall portion (10b). The upper wall portion (10a) is connected to the cylinder block (6), and upper wall bosses (11) and (11) are provided on the left and right sides of the upper wall portion (10a). The upper end of the cylinder is connected to the left and right sides (2c) and (2c) of the lower part (2b) of the wall between the cylinders (2),
A bearing bolt (12) penetrated through the lower wall portion (10b) is inserted into the upper wall boss (11), and one of the upper wall boss (11) and the lower side portion (2b) between the cylinder wall (2) or A multi-cylinder engine in which a lower female thread portion (13) is provided over both, a bearing bolt (12) is screwed onto the lower female thread portion (13), and the lower wall portion (10b) is assembled to the cylinder block (6). .

  In this type of engine, the cylinder head (4) is lifted upward by the gas pressure generated in the combustion chamber, and the lower wall portion (10b) is pulled downward, so that the upper female thread portion (9) is a head bolt (8). ) And the lower female thread portion (13) is pulled downward by the bearing bolt (12).

Conventionally, there are multi-cylinder engines having the above-described technology.
However, in this type of engine, generally, an upper female screw portion and a lower female screw portion are formed on the outer wall of the cylinder block.

The above prior art has the following problems.
<Problem 1> The outer wall of the cylinder block tends to vibrate.
Since the upper female screw portion and the lower female screw portion are formed on the outer wall of the cylinder block, the outer wall of the cylinder block is stretched by the gas pressure generated in the combustion chamber and easily vibrates. For this reason, the engine noise increases and the service life of the engine is shortened.
In order to solve the problem 1, as in the present invention, as shown in FIG. 1, the space in the cylinder block is formed between the upper and lower internal thread portions (9), (13) and the outer wall (14) of the cylinder block (6). It is effective to interpose (17). However, in this case, the gas pressure borne by the outer wall (14) of the cylinder block (6) is affected by the left and right sides (2c) (2c) of the lower part (2b) of the inter-cylinder wall (2) and its Since it is applied to the left and right peripheral wall portions (15) and (15) on the lower side of the cylinder wall (1) connected to the front and rear, if this portion is thin, the following new problem may occur.

<Problem 2> Distortion of the left and right peripheral walls near the bottom of the cylinder wall increases.
When the thickness of the left and right peripheral wall portions near the bottom of the cylinder wall is thin, the distortion in this portion increases, and piston seizure, slap noise, and the like occur.

  The subject of this invention is providing the multicylinder engine which can solve the said problem.

The configuration of the invention of claim 1 is as follows.
In the multi-cylinder engine described in the background of the invention,
As shown in FIG. 1, a cylinder block inner space (17) is interposed between the upper and lower internal thread portions (9) and (13) and the outer wall (14) of the cylinder block (6).
As shown in FIGS. 3 and 4, the left and right sides (2c) (2c) of the lower portion (2b) of the inter-cylinder wall (2) and the lower left and right sides of the cylinder wall (1) connected to the front and rear thereof Of the peripheral wall portions (15) and (15), as the left and right peripheral wall portions (15) and (15) approach the left and right side portions (2c) and (2c), the thickness thereof is gradually increased.
As shown in FIG. 6, a side water channel (34) is provided on one of the left and right outer walls (14) of the cylinder block (6) along the front-rear direction, and a water jacket (16) is provided in the cylinder block (6). Water is introduced into the water jacket (16) through the side water channel (34),
As shown in FIG. 6, a pair of upper and lower secondary rotary balancer shaft storage chambers (35) and a valve camshaft (22) are placed on one side of the left and right outer walls (14) of the cylinder block (6). The side water channel (34), a pair of upper and lower secondary rotating balancer shaft storage chambers (35), and a valve operating cam shaft (22) are disposed along the water jacket (16) and the cylinder wall (1). A pair of upper and lower secondary rotating balancer shaft storage chambers (35) and a valve operating cam shaft (22) are arranged vertically on the side water channel (34).
The valve camshaft (22) is disposed below the side water channel (34), and the secondary rotary balancer shaft storage chamber (35) is disposed above the side water channel (34).
Of the left and right outer walls (14) of the cylinder block (6), another pair of upper and lower secondary rotation balancer shaft accommodating chambers (35) and the outer wall (14) opposite to the valve operating cam shaft (22) Arrange the storage chamber (36) for the next rotation balancer shaft,
The multi-cylinder engine is characterized in that the other secondary rotation balancer shaft accommodating chamber (36) is disposed at a position lower than the valve operating cam shaft (22).

(Invention of Claim 1)
The invention of claim 1 has the following effects.
<Effect 1> The outer wall of the cylinder block hardly vibrates.
As shown in FIG. 1, since the cylinder block inner space (17) is interposed between the upper and lower internal thread portions (9) and (13) and the outer wall (14) of the cylinder block (6), the outer wall of the cylinder block (6) is removed. (14) is not easily stretched by the gas pressure generated in the combustion chamber, and is difficult to vibrate. For this reason, the engine noise is reduced and the service life of the engine is also increased.

<Effect 2> Distortion of the left and right peripheral wall portions on the lower side of the cylinder wall can be suppressed.
As shown in FIGS. 3 and 4, the left and right sides (2c) (2c) of the lower portion (2b) of the inter-cylinder wall (2) and the lower left and right sides of the cylinder wall (1) connected to the front and rear thereof As the left and right peripheral wall portions (15) and (15) of the peripheral wall portions (15) and (15) approach the left and right side portions (2c) and (2c), the thickness of the cylinder wall (1) is gradually increased. Even if a large gas pressure is applied to the lower left and right peripheral wall portions (15) and (15), the distortion of this portion can be suppressed. For this reason, generation | occurrence | production of the seizing of a piston, the slap sound, etc. resulting from the distortion of this part can be suppressed.

(Invention of Claim 2)
In addition to the effect of the invention of claim 1, the invention of claim 2 has the following effect.
<Effect 3> The strength of the lower portion of the wall between the cylinders can be secured.
As shown in FIG. 1, the lowermost edge (20) of the transverse water channel (18) is positioned higher than the position (19) of the uppermost piston ring of the piston head located at the bottom dead center. The height of the lower portion (2b) of the meat wall (2) can be sufficiently secured, and the strength of this portion can be secured.

(Invention of Claim 3 )
The invention of claim 3 has the following effect in addition to the effect of the invention of claim 1 or claim 2 .
<Effect 6> The lower portion of the wall between the cylinders can be effectively used.
As shown in FIG. 1, since the oil supply passage (21) passes between the upper female screw portion (9) and the lower female screw portion (13), the lower portion of the inter-cylinder wall (2) ( 2b) can be effectively used as a wall for forming the oil supply passage (21).

<Effect 7> It is possible to suppress the chips generated during screw machining from entering the oil supply passage.
As shown in FIG. 1, since the oil supply passage (21) does not communicate with the upper female screw portion (9) and the lower female screw portion (13), chips generated during threading enter the oil supply passage (21). Can be suppressed.

(Invention of Claim 4 )
The invention of claim 4 has the following effect in addition to the effect of the invention of any one of claims 1 to 3 .
<Effect 8> The lower portion of the wall between the cylinders can be effectively used.
As shown in FIG. 1, the valve camshaft (22) is inserted between the upper female screw portion (9) and the lower female screw portion (13) at the lower portion (2b) of the cylinder wall (2). Therefore, the lower portion (2b) of the inter-cylinder wall (2) can be effectively used as a wall for forming the accommodating portion of the valve drive cam shaft (22) .

(Invention of Claim 5 )
The invention of claim 5 has the following effect in addition to the effect of the invention of any one of claims 1 to 4 .
<Effect 9> Different engines can be easily created.
As shown in FIG. 1, in order to divide the cylinder block (6) into an upper block portion (6a) and a lower block portion (6b), a plurality of types of lower block portions (6b) are prepared. By selectively assembling the upper block portion (6a), it is possible to easily produce different types of engines. For example, by preparing a lower block part (6b) with a wide standard specification and a lower block part (6b) with a narrow tractor specification, and assembling them selectively to the upper block part (6a), The standard engine and the tractor engine can be easily separated.

(Invention of Claim 6 )
The invention of claim 6 has the following effect in addition to the effect of the invention of claim 5 .
<< Effect 10 >> It is possible to reduce the burden on the left and right side portions of the lower portion of the wall between the cylinders.
As shown in FIG. 6, since the lower wall portion (10b) of the bearing wall (10) is connected to the lower block portion (6b), the gas pressure generated in the combustion chamber is lower than the wall between the cylinders (2). Not only the left and right sides of the part (2b) but also the upper block part (6a) is borne through the lower block part (6b). For this reason, it is possible to reduce the burden on the left and right sides of the lower portion (2b) of the inter-cylinder wall (2).

<< Effect 11 >> The sealing force of the mating surfaces of the upper and lower block portions is high.
As shown in FIG. 6, since the lower wall portion (10b) of the bearing wall (10) is connected to the lower block portion (6b), the sealing of the mating surfaces of the upper and lower block portions (6a) (6b) is assembled into the block. Since both the bolt (24) and the bearing bolt (12) are used, the sealing force of the mating surfaces of the upper and lower block portions (6a) (6b) is high.

(Invention of Claim 7 )
The invention of claim 7 has the following effect in addition to the effect of the invention of claim 5 or 6 .
<Effect 12> The rigidity of the cylinder block is high.
As shown in FIGS. 4 and 5, the left and right outer walls (14) of the cylinder block (6) are moved along the outer shape of the connecting rod (25) and the crank arm (26) passing near the left and right outer walls (14). Since it is bent, the cylinder block (6) has high rigidity.
<< Effect 13 >> The sealing force of the mating surfaces of the upper and lower block portions is enhanced.
As shown in FIGS. 4 and 5, since the mounting bosses (28a) and (28b) of the block mounting bolt (24) are formed on the inner wall portion (27) retracted inward, the left and right mounting bosses (28a) (28b) approaches each other, and the sealing force of the mating surfaces of the upper and lower block portions (6a) and (6b) is strengthened.
(Invention of Claim 8 )
In addition to the effect of the invention according to any one of claims 1 to 7 , the following effect is achieved.
<< Effect 14 >> The thickness of the left and right peripheral wall portions of the cylinder wall near the wall between the cylinders can be sufficiently secured.
As shown in FIG. 4, the increase in the thickness of the left and right peripheral wall portions (15) and (15) on the lower side of the cylinder wall (1) is caused by the longitudinal center portion (15a) of the left and right peripheral wall portions (15) and (15). Since it started from (15a), the thickness of the left and right peripheral wall portions (15), (15) of the cylinder wall (1) near the inter-cylinder wall (2) can be sufficiently taken.
(Invention of Claim 9 )
In addition to the effects of the invention according to any one of claims 1 to 8 , the following effects are provided.
<< Effect 15 >> Thicknesses of the left and right peripheral wall portions of the cylinder wall near the cylinder wall can be sufficiently secured.
As shown in FIG. 4, the front and rear center portions (15a) and (15a) of the left and right peripheral wall portions (15) and (15) are formed on both outward facing surfaces (15b) and (15b) of the left and right peripheral wall portions (15) and (15). Left and right side portions (2c) (2c) gradually form an outwardly widening shape away from the crankshaft center axis (5a), so that the left and right peripheral wall portions of the cylinder wall (1) near the inter-cylinder wall (2) (15) The thickness of (15) can be taken sufficiently.
(Invention of Claim 10 )
In addition to the effects of the invention according to any one of claims 1 to 9 , the following effects are provided.
<< Effect 16 >> The thickness of the left and right peripheral walls of the cylinder wall near the wall between the cylinders can be sufficiently increased, and the cylinder wall can be easily molded.
The entire outer surfaces (15b) (15b) of the left and right peripheral wall portions (15), (15) on the lower side of the cylinder wall (1) are formed substantially straight along the front-rear direction. ) The left and right peripheral wall portions (15) and (15) of the cylinder wall (1) in the vicinity can be made sufficiently thick, and the cylinder wall (1) can be easily molded.
(Invention of Claim 11)
The invention of claim 11 has the following effect in addition to the effect of the invention of any one of claims 1 to 10.
<Effect 4> The shear strain of the lower portion of the wall between the cylinders can be suppressed.
As shown in FIG. 1, a pair of head bolts (8) and bearing bolts (12) positioned above and below are arranged on the same axis (29), so that the lower wall between the cylinders (2) is lower. The tensile force received by the portion (2b) acts on the same axis (29), and the shear strain of the lower portion (2b) of the inter-cylinder wall (2) can be suppressed. For this reason, it is possible to suppress the occurrence of piston seizure, slap noise, and the like due to the shear strain of this portion.
(Invention of Claim 12)
The invention of claim 12 has the following effects in addition to the effects of the invention of any one of claims 1 to 11.
<Effect 5> Parts management becomes easy and parts costs are reduced.
As shown in FIG. 1, since the head bolt (8) and the bearing bolt (12) are made common, the bolt management becomes easy and the procurement cost of the bolt becomes low.

  Embodiments of the present invention will be described with reference to the drawings. FIGS. 1 to 6 are diagrams for explaining an embodiment of the present invention. In this embodiment, a vertical water-cooled in-line multi-cylinder diesel engine will be described.

The configuration of this engine is as follows.
As shown in FIG. 6, the cylinder head (4) is assembled to the upper part of the cylinder block (6), the head cover (40) is assembled to the upper part of the cylinder head (4), and the oil pan (37 ).

The assembly structure of the cylinder head (4) is as follows.
As shown in FIG. 2, adjacent cylinder walls (1) (1) are connected to each other to form an inter-cylinder wall (2). As shown in FIG. 1, the direction of the cylinder center axis (3) is the vertical direction, the cylinder head (4) is upward, the width direction of the cylinder block (6) is the horizontal direction, and the installation direction of the crankshaft (5) is Inter-cylinder bosses (7) and (7) are provided on the left and right sides of the upper part (2a) of the inter-cylinder wall (2) when viewed in the front-rear direction. It is made to continue with the upper part of the right and left both sides of the lower part (2b) of the interstitial wall (2).

  As shown in FIG. 1, a head bolt (8) passed through the cylinder head (4) is inserted into the inter-cylinder boss (7), and an upper female thread portion (9) is provided on the inter-cylinder boss (7). A head bolt (8) is screwed onto the female thread portion (9), and the cylinder head (4) is assembled to the cylinder block (6). The upper female thread portion (9) can be formed over one or both of the inter-cylinder boss (7) and the lower portion (2b) of the inter-cylinder wall (2).

The assembly structure of the cylinder block (6) is as follows.
As shown in FIG. 1, a bearing wall (10) of the crankshaft (5) is formed in the crankcase of the cylinder block (6), and the bearing wall (10) is divided into an upper wall portion (10a) and a lower wall portion ( 10b), the upper wall portion (10a) is connected to the cylinder block (6), and upper wall bosses (11) and (11) are provided on both the left and right sides of the upper wall portion (10a). The upper portions of the bosses (11) and (11) are connected to the lower portions of the left and right side portions (2c) and (2c) of the lower portion (2b) of the inter-cylinder wall (2). A bearing bolt (12) penetrating the lower wall portion (10a) is inserted into the upper wall boss (11), and a lower female screw portion (13) is provided on the upper wall boss (11). A bearing bolt (12) is screwed and the lower wall portion (10b) is assembled to the cylinder block (6). The lower female thread portion (13) can be formed over one or both of the upper wall boss (11) and the lower portion (2b) of the inter-cylinder wall (2).

The device concerning the cylinder block (6) is as follows.
As shown in FIGS. 1 and 2, a cylinder block inner space (17) is interposed between the upper and lower female thread portions (9) and (13) and the outer wall (14) of the cylinder block (6). For this reason, the outer wall (14) of the cylinder block (6) is hardly stretched by the gas pressure generated in the combustion chamber, and is difficult to vibrate. For this reason, the engine noise is reduced and the service life of the engine is also increased. Also, the left and right side portions (2c) (2c) of the lower portion (2b) of the lower wall (2) between the cylinders, and the left and right peripheral wall portions (15), (15) of the lower portion of the cylinder wall (1) connected to the front and rear thereof. Of these, as the left and right peripheral wall portions (15) and (15) approach the left and right side portions (2c) and (2c), the thickness thereof is gradually increased. For this reason, even if a large gas pressure is applied to the left and right peripheral wall portions (15) and (15) on the lower side of the cylinder wall (1), the distortion of this portion can be suppressed. For this reason, generation | occurrence | production of the seizing of a piston, the slap sound, etc. resulting from the distortion of this part can be suppressed. The cylinder block inner space (17) is an oil dropping space and a push rod accommodating chamber.
The increase in thickness of the left and right peripheral wall portions (15) and (15) on the lower side of the cylinder wall (1) is started from the front and rear central portions (15a) and (15a) of the left and right peripheral wall portions (15) and (15). ing. The left and right sides (2c) (2c) of the lower part (2b) of the lower wall (2b) between the cylinders and the left and right peripheral walls (15), (15) of the lower part of the cylinder wall (1) connected to the front and rear thereof. The left and right peripheral walls (15) and (15) have both outward facing surfaces (15b) and (15b) extending from the center portions (15a) and (15a) in the front and rear direction of the left and right peripheral walls (15) and (15). As it approaches 2c) and 2c, it is formed in an outwardly expanding shape that gradually gets away from the crankshaft central axis (5a) . However, the extent of the spread is slight, and when the cylinder block (6) is viewed from directly below, both the outward facing surfaces (15b) (15b) of the left and right peripheral wall portions (15) (15) on the lower side of the cylinder wall (1). ) Is formed substantially straight along the front-rear direction. For this reason, the left and right peripheral wall portions (15) and (15) of the cylinder wall (1) near the wall between the cylinders (2) can be sufficiently thick, and the cylinder wall (1) can be easily molded. Become.
In general, the front and rear center portions (15a) and (15a) of the left and right peripheral wall portions (15) and (15) are regions located equidistant from a pair of adjacent cylinder wall surfaces (2) and (2), This is a region where D / 3 is the front-rear dimension d, where D is the distance between the centers of the pair of cylinder wall (2) and (2). From the viewpoint of sufficiently securing the thickness of the left and right peripheral wall portions (15) and (15) near the wall between the cylinders (2), the increase in the thickness of the left and right peripheral wall portions (15) and (15) (15a) Start from (15a), especially starting from an area located equidistant from the adjacent pair of cylinder wall (2) and (2), whose front and rear dimensions are less than D / 4 It is desirable to start from an area below D / 6, and most preferably from an area below D / 8.

  As shown in FIG. 1, in forming the transverse channel (18) in the inter-cylinder wall (2), the crossing is performed at a position higher than the position (19) of the uppermost piston ring of the piston head located at the bottom dead center. The lowermost edge (20) of the water channel (18) is located. For this reason, the height of the lower part (2b) of the wall between the cylinders (2) can be sufficiently secured, and the strength of this part can be secured.

  As shown in FIG. 1, a pair of head bolts (8) and bearing bolts (12) positioned vertically are arranged on the same axis (29). For this reason, the tensile force received by the lower portion (2b) of the inter-cylinder wall (2) acts on the same axis (29), and the shear strain of the lower portion (2b) of the inter-cylinder wall (2) is reduced. Can be suppressed. For this reason, it is possible to suppress the occurrence of piston seizure, slap noise, and the like due to the shear strain of this portion. Further, the head bolt (8) and the bearing bolt (12) are made common. For this reason, bolt management becomes easy, and the procurement cost of the bolt becomes low.

As shown in FIG. 1, when the oil supply passage (21) is formed in the lower portion (2b) of the inter-cylinder wall (2), the oil supply passage (21) includes an upper female screw portion (9) and a lower female screw. It passes between these, without communicating with a part (13). For this reason, the lower portion (2b) of the inter-cylinder wall (2) can be effectively used as a wall for forming the oil supply passage (21). Further, it is possible to suppress the chips generated during the screw processing from entering the oil supply passage (21). The valve camshaft (22) is inserted between the upper female screw portion (9) and the lower female screw portion (13) at the lower portion (2b) of the cylinder wall (2). For this reason, the lower portion (2b) of the inter-cylinder wall (2) can be effectively used as a wall for forming the accommodating portion of the valve operating cam shaft (22) . Reference numeral (23) in the figure denotes a shaft hole of the valve operating cam shaft (22).

  As shown in FIG. 1, the cylinder block (6) can be divided into an upper block portion (6a) and a lower block portion (6b), and the lower block portion (6b) is blocked by a block mounting bolt (24). (6a) can be assembled. For this reason, by preparing a plurality of types of lower block portions (6b) and selectively assembling them into the upper block portion (6a), different engines can be easily separated. For example, by preparing a lower block part (6b) with a wide standard specification and a lower block part (6b) with a narrow tractor specification, and assembling them selectively to the upper block part (6a), The standard engine and the tractor engine can be easily separated.

  As shown in FIG. 1, the lower wall portion (10b) of the bearing wall (10) is connected to the lower block portion (6b). For this reason, the gas pressure generated in the combustion chamber rises not only through the left and right sides (2c) (2c) of the lower part (2b) of the wall between the cylinders (2) but also through the lower block part (6b). The block portion (6a) is also borne. For this reason, the burden concerning the right and left side parts (2c) (2c) of the lower part (2b) of the cylinder wall (2) can be reduced. In addition, since the sealing of the mating surfaces of the upper and lower block portions (6a) and (6b) is performed by both the block assembly bolt (24) and the bearing bolt (12), the mating surfaces of the upper and lower block portions (6a) and (6b) High sealing power.

  As shown in FIGS. 4 and 5, the left and right outer walls (14) of the cylinder block (6) are moved along the outer shape of the connecting rod (25) and the crank arm (26) passing near the left and right outer walls (14). It is bent. For this reason, the cylinder block (6) has high rigidity. Of the left and right outer walls (14), upper and lower mounting bosses (28a) (28b) of the block mounting bolt (24) are formed on the inner wall portion (27) retracted inward. For this reason, the left and right mounting bosses (28a) and (28b) approach each other, and the sealing force of the mating surfaces of the upper and lower block portions (6a) and (6b) is strengthened.

  As shown in FIG. 6, in forming the lower mounting boss (28b) that allows the block assembly bolt (24) to pass through the lower block portion (6b), the lower opening of the lower mounting boss (28b) It opens in the part (6b) or the oil pan (37). For this reason, the oil that has entered the boss hole of the lower mounting boss (28b) returns from the lower opening to the oil pan (37) and does not leak out of the engine. Further, when sealing the mating surfaces of the upper and lower block portions (6a) and (6b), an adhesive may be applied to the mating surfaces, but oil may enter the boss holes of the lower mounting boss (28b). However, since the oil does not leak out of the engine, it is not necessary to apply an adhesive around the entire upper opening of the lower mounting boss (28b). For this reason, it does not take time to seal the mating surfaces of the upper and lower block portions.

The mounting structure of the oil level gauge (31) is as follows.
As shown in FIGS. 5 and 6, the insertion boss (32) of the oil level gauge (31) is disposed in the recessed space (30) facing the inner wall portion (27) from the outside. . For this reason, the width of the cylinder block (6) can be reduced. Further, the insertion boss (32) of the oil level gauge (31) is arranged on the side of the bearing wall (10) of the crankshaft (5). For this reason, the oil level gauge (31) can be inserted into the left and right center of the oil pan (37) while avoiding the rotating crank arm (26) and connecting rod (25). For this reason, the oil level can be accurately detected even when the engine is tilted left and right.

  As shown in FIG. 5, the unperforated boss meat portion (33) for forming the insertion boss (32) of the oil level gauge (31) is formed into recessed spaces (33) at a plurality of locations on the left and right outer walls (14). 30). For this reason, it is possible to select the mounting position of the oil level gauge (31). Further, the rigidity of the cylinder block (6) is increased.

Another structure for strengthening the rigidity of the cylinder block (6) is as follows.
As shown in FIG. 3, a side water channel (34) along the front-rear direction is provided on one of the left and right outer walls (14) of the cylinder block (6), and a water jacket (16) is provided in the cylinder block (6). When the cooling water is introduced into the water jacket (16) through the side water channel (34), as shown in FIG. 6, a part of the outer wall (14) of the cylinder block (6) is curved outwardly. The side water channel (34) is formed inside. In providing the secondary rotation balancer shaft accommodating chambers (35) and (36) along the front-rear direction on both the left and right outer walls (14) of the cylinder block (6), a part of the outer wall (14) of the cylinder block (6) is removed. A secondary rotating balancer shaft accommodating chamber (35) (36) is formed on the inner side thereof so as to curve outwardly. The secondary rotary balancer shaft accommodating chambers (35) (36) contains a secondary rotary balancer shaft (38) (39).
The structure of the side waterway and its surroundings is as follows.
As shown in FIG. 6, a pair of upper and lower secondary rotary balancer shaft storage chambers (35) and a valve camshaft (22) are placed on one side of the left and right outer walls (14) of the cylinder block (6). The side water channel (34), a pair of upper and lower secondary rotating balancer shaft storage chambers (35), and a valve operating cam shaft (22) are disposed along the water jacket (16) and the cylinder wall (1). A pair of upper and lower secondary rotation balancer shaft storage chambers (35) and a valve operating cam shaft (22) are arranged in an up-and-down manner along the side water channel (34).
The valve camshaft (22) is disposed below the side water channel (34), the secondary rotary balancer shaft storage chamber (35) is disposed above the side water channel (34), and the cylinder block (6) Among the left and right outer walls (14), another secondary rotary balancer shaft housing is accommodated in the upper wall (14) opposite to the pair of upper and lower secondary rotational balancer shaft housings (35) and the valve operating cam shaft (22). The chamber (36) is disposed, and the other secondary rotation balancer shaft accommodating chamber (36) is disposed at a position lower than the valve operating cam shaft (22).

It is a vertical front view of a cylinder head of a cylinder block of an engine concerning an embodiment of the present invention. It is a top view of the cylinder block of the engine concerning the embodiment of the present invention. It is the III-III sectional view taken on the line of FIG. It is the IV-IV sectional view taken on the line of FIG. It is the VV sectional view taken on the line of FIG. 1 is a longitudinal front view of an engine according to an embodiment of the present invention.

Explanation of symbols

(1) ... Cylinder wall, (2) ... Inter-cylinder wall, (2a) Upper part, (2b) Lower part, (2c) (2c) Left and right sides, (3) Cylinder center axis , (4) Cylinder head, (5) Crankshaft, (6) Cylinder block, (6a) Upper block, (6b) Lower block, (7) Cylinder boss, (8) Head bolt, (9) Upper female thread, (10) Bearing wall, (10a) Upper wall part, (10b) Lower wall part, (11) Upper wall boss, (12) Bearing bolt, ( 13) Lower female thread, (14) Outer wall, (15) Lower left and right peripheral walls of the cylinder wall, (16) Water jacket, (17) Cylinder block inner space, (18) Transverse water channel, ( 19) Position of the uppermost piston ring, (20) Bottom edge of the transverse channel, (21) Oil supply passage, (22) Valve camshaft , (24) Block assembly bolt (25) ... Connecting rod, (26) ... Crank arm, (27) ... Inward wall portion, (28a) (28b) ... Upper and lower mounting bosses of block assembly bolts, (34) ... Side waterway, (35) (36) ··· Storage chamber for secondary rotation balancer shaft .

Claims (12)

Adjacent cylinder walls (1) and (1) are connected to form an inter-cylinder wall (2), the cylinder center axis (3) is in the vertical direction, the cylinder head (4) is in the upward direction, and the cylinder block Looking at the width direction of (6) as the left-right direction and the installation direction of the crankshaft (5) as the front-rear direction,
Inter-cylinder bosses (7) and (7) are provided on the left and right sides of the upper part (2a) of the inter-cylinder wall (2), and these inter-cylinder bosses (7) and (7) are placed under the inter-cylinder wall (2). The left and right sides (2c) (2c) of the side portion (2b) are connected to each other,
Insert the head bolt (8) that penetrates the cylinder head (4) into the boss (7) between cylinders, and either or both of the boss (7) between cylinders and the lower part (2b) of the wall between cylinders (2). An upper female thread portion (9) is provided, and a head bolt (8) is screwed onto the upper female thread portion (9), and the cylinder head (4) is assembled to the cylinder block (6).
A bearing wall (10) of the crankshaft (5) is formed in the crankcase of the cylinder block (6), and the bearing wall (10) can be divided into an upper wall portion (10a) and a lower wall portion (10b). The upper wall portion (10a) is connected to the cylinder block (6), and upper wall bosses (11) and (11) are provided on the left and right sides of the upper wall portion (10a). To the left and right sides (2c) (2c) of the lower part (2b) of the wall between the cylinders (2),
A bearing bolt (12) penetrated through the lower wall portion (10b) is inserted into the upper wall boss (11), and one of the upper wall boss (11) and the lower side portion (2b) between the cylinder wall (2) or A multi-cylinder engine in which a lower female thread portion (13) is provided over both, a bearing bolt (12) is screwed onto the lower female thread portion (13), and the lower wall portion (10b) is assembled to the cylinder block (6). In
A cylinder block inner space (17) is interposed between the upper and lower female thread portions (9) (13) and the outer wall (14) of the cylinder block (6),
Of the left and right side portions (2c) (2c) of the lower portion (2b) of the lower wall portion (2) between the cylinders, and the left and right peripheral wall portions (15), (15) of the lower portion of the cylinder wall (1) connected to the front and rear thereof As the left and right peripheral wall portions (15) and (15) approach the left and right side portions (2c) and (2c), the thickness gradually increases .
A side water passage (34) along the front-rear direction is provided on one of the left and right outer walls (14) of the cylinder block (6), a water jacket (16) is provided in the cylinder block (6), and cooling water from the radiator is supplied to the side water passage ( 34) through the water jacket (16),
A pair of upper and lower secondary rotating balancer shaft storage chambers (35) and a valve operating cam shaft (22) are arranged along with a side water channel (34) on one of the left and right outer walls (14) of the cylinder block (6). (34) and a pair of upper and lower secondary rotating balancer shaft accommodating chambers (35) and a valve operating cam shaft (22) are arranged vertically along the water jacket (16) and the cylinder wall (1). The secondary rotation balancer shaft storage chamber (35) and the valve operating cam shaft (22) are arranged separately above and below the side water channel (34),
The valve camshaft (22) is disposed below the side water channel (34), and the secondary rotary balancer shaft storage chamber (35) is disposed above the side water channel (34).
Of the left and right outer walls (14) of the cylinder block (6), another pair of upper and lower secondary rotation balancer shaft accommodating chambers (35) and the outer wall (14) opposite to the valve operating cam shaft (22) Arrange the storage chamber (36) for the next rotation balancer shaft,
The multi-cylinder engine is characterized in that the other secondary rotation balancer shaft accommodating chamber (36) is disposed at a position lower than the valve operating cam shaft (22) . The multi-cylinder engine according to claim 1,
In forming the transverse channel (18) in the wall between the cylinders (2), the lowest position of the transverse channel (18) is higher than the position (19) of the uppermost piston ring of the piston head located at the bottom dead center. A multi-cylinder engine characterized in that the rim (20) is located. The multi-cylinder engine according to claim 1 or 2 ,
In forming the oil supply passage (21) in the lower portion (2b) between the cylinder wall (2), the oil supply passage (21) communicates with the upper female screw portion (9) and the lower female screw portion (13). The multi-cylinder engine is characterized in that it passes between these without being carried out. The multi-cylinder engine according to any one of claims 1 to 3 ,
The valve camshaft (22) is inserted between the upper female screw part (9) and the lower female screw part (13) at the lower part (2b) between the cylinder wall (2). Multi-cylinder engine. The multi-cylinder engine according to any one of claims 1 to 4 ,
The cylinder block (6) can be divided into an upper block portion (6a) and a lower block portion (6b), and the lower block portion (6b) can be assembled to the upper block portion (6a) with a block assembly bolt (24). A multi-cylinder engine characterized by that. The multi-cylinder engine according to claim 5 ,
A multi-cylinder engine, wherein a lower wall portion (10b) of the bearing wall (10) is connected to a lower block portion (6b). The multi-cylinder engine according to claim 5 or 6 ,
The left and right outer walls (14) of the cylinder block (6) are bent along the outer shape of the connecting rod (25) and the crank arm (26) passing near the left and right outer walls (14), and the left and right outer walls (14). The multi-cylinder engine is characterized in that mounting bosses (28a) (28b) of the block mounting bolt (24) are formed on the inner wall portion (27) retracted inside. The multi-cylinder engine according to any one of claims 1 to 7 ,
The increase in thickness of the left and right peripheral wall portions (15) and (15) on the lower side of the cylinder wall (1) is started from the front and rear central portions (15a) and (15a) of the left and right peripheral wall portions (15) and (15). Multi-cylinder engine characterized by that. A multi-cylinder engine according to any one of claims 1 to 8,
Looking at the cylinder block (6) from directly below,
The left and right sides (2c) (2c) of the lower part (2b) of the lower wall (2b) between the cylinders and the left and right peripheral walls (15), (15) of the lower part of the cylinder wall (1) connected to the front and rear thereof. The left and right peripheral walls (15) and (15) have both outward facing surfaces (15b) and (15b) extending from the center portions (15a) and (15a) of the left and right peripheral walls (15) and (15) to both left and right ends ( 2c) A multi-cylinder engine characterized by being formed in an outwardly expanding shape that gradually moves away from the crankshaft central axis (5a) as approaching (2c). The multi-cylinder engine according to any one of claims 1 to 9 ,
Looking at the cylinder block (6) from directly below,
The whole of the outwardly facing surfaces (15b) (15b) of the left and right peripheral wall portions (15), (15) on the lower side of the cylinder wall (1) are formed substantially straight along the front-rear direction. Multi-cylinder engine. The multi-cylinder engine according to any one of claims 1 to 10 ,
A multi-cylinder engine characterized in that a pair of head bolts (8) and bearing bolts (12) positioned above and below are arranged on the same axis (29). The multi-cylinder engine according to any one of claims 1 to 11 ,
A multi-cylinder engine characterized by having a head bolt (8) and a bearing bolt (12) in common.