KR100496057B1 - Cooling system of multi cylinder cylinder - Google Patents

Abstract

The channel forming member 10 injected into the continuous wall portion 4 between the adjacent bores 3a and 3a of the multi-cylinder cylinder 2 includes the cylinder jackets 8 and 8 and the head jacket in the cylinder block 1. 22, a pair of jacket communication paths (12. 12) left and right in communication with each other in the longitudinal direction, the cooling water passage (15) of the upper and lower abdomen means for communicating the pair of jacket communication paths (12, 12), and the cooling water passages of the plurality of stages ( 15) and a plurality of stages of non-cavities 11 alternately formed, and a pair of left and right coolant introduction portions 13 and 13 are directed toward the respective cylinder jackets 8 and 8 at the lower portion of the jacket communication paths 12 and 12. The opening and closing of the left and right pairs of coolant introduction portions 13.13 are arranged along the outer circumferential surfaces 3a and 3a of the front and rear pairs of coolant guide plates 14 and 14 protruding from the left and right, respectively. Open wide to compose.

Description

Chiller of multi-cylinder cylinder

The present invention relates to a cooling device for a multi-cylinder cylinder of a multi-cylinder engine, and more particularly, a channel forming member is provided in a continuous six-wall portion between adjacent bores of the multi-cylinder cylinder. The present invention relates to a technique of injecting a constituent caplet, and circulating cooling water to the channel forming member so as to strongly cool the head assembly of the continuous six wall portion.

In recent years, the necessity of miniaturizing and reducing the weight of a multi-cylinder engine reduces the gap between cylinder bores, or increases the engine bore by increasing the displacement, thereby increasing the cylinder bore to make the continuous wall of the cylinder as thin as possible. One multi-cylinder cylinder has been employed.

As a prior art of this kind. For example, those disclosed in Japanese Unexamined Patent Publication No. 56-42744 (hereinafter referred to as conventional example (1)) and those disclosed in Japanese Unexamined Patent Publication No. 59-68155 (hereinafter referred to as conventional example (2)). In addition, what is disclosed in Japanese Unexamined Patent Application Publication No. 59-107946 (hereinafter, referred to as conventional example (3)) is known.

10 (A), (B), and (C) show a conventional example (1). FIG. 10 (A) is a longitudinal cross-sectional view of the principal part of the multicylinder cylinder, FIG. 10 (B) is a transverse plan view in the direction of the arrow BB in FIG. 10 (A), and FIG. Injection into continuous meat wall between bores Is a perspective view of the channel forming member.

In the conventional example (1), a plurality of cylinders (53) are placed in the cylinder block (51) before and after, and adjacent cylinders (53, 53) are continuous by the continuous oil wall portion (54) to constitute a multi-cylinder cylinder (52). The cylinder jacket 58 is formed so as to surround the multi-cylinder cylinder 52, and the channel forming member 110 is injected into the continuous six wall portion 54. As shown in Figs. 10A, 10B, and 10C, the channel forming member 110 has a longitudinal, long, flat cooling water channel 115 as viewed from the longitudinal side. And the cylinder jackets 58 and 58 at the left and right ends of the head assembly 54 are communicated with the cooling water 115.

As shown in FIG. 10 (B), the cylinder jackets 58, 58 are narrowed on both the left and right sides of the head assembly portion 54a of the continuous six wall portion 54, and the The cooling water introduced from one side cools the head assembly 54a by circulating the cooling water passage 115. In addition, the bosses of the left and right pair of bolts 56 and 56 for fastening the cylinder head (not shown) are located outside the corresponding cylinder jackets 58 and 58. Here, the protruding stop portions 114 and 114 protruding from the left and right ends of the channel forming member 110 are used to securely fix the channel forming member 110 to the inside when the cylinder jacket is manufactured.

The said prior art example (1). Since the left and right ends and the protruding stop portions 114 and 114 of the cooling water passage 11 protrude into the cylinder jackets 58 and 58, the smooth flow of the cooling water flowing along the cylinder outer peripheral surface 53b is inhibited. Cooling water is hindered from entering the cooling water path 115. For this reason, there is a difficulty in that the head assembly 54a of the continuous wall portion 54 cannot be cooled strongly.

In addition, since the cooling water passage 115 is flat and long in length, in the machining of the cylinder bore 53a, a lack of strength is generated in the corresponding portion of the cooling water passage 115, and further, the localization of the cylinder bore 53a is performed. It may cause distortion. In order to avoid this, it is necessary to make the circumferential thickness of the said continuous oil wall part 4 into some thickness. As a result, since the circumferential thickness of the continuous ground wall portion 54 cannot be made sufficiently thin, it is difficult to narrow the interval between the cylinder bores 53a and increase the displacement so as to further increase the engine output.

In addition, since the left and right cylinder head fastening bosses 55 and 55 are located outside the cylinder jackets 58 and 58, the space between the left and right head bolts 56 and 56 is increased, and the cylinder 53 is circumferentially directed. Depending on the uniformity, there is a difficult point that can not be tightened strongly.

11 (A), (B), and (C) show a conventional example (2), and FIG. 11 (A) is a longitudinal sectional view of an essential part of a multi-cylinder cylinder, and FIG. 11 (B) is a Fig. 11 (C) is a perspective view of the channel forming member injected into the connecting six wall portion 54 of the multi-cylinder cylinder.

The channel forming member 110 uses the left and right cylinder jackets 58 and 58 and the head jacket (not shown) in the cylinder block 51 as shown in FIGS. 11A, 11B, and 11C. A pair of left and right jacket communication paths 112 and 112 communicating with each other, a cooling water path 115 communicating with the left and right jacket communication paths 112 and 112, and respective jacket communication paths 112 and 112, respectively. Located at the lower side, a pair of left and right cooling water introduction parts 113 and 113 opened toward the cylinder jackets 58 and 58 are provided.

The cooling water introduced from the cooling water introduction parts 113 and 113 flows through the cooling water path 115 and is located at an upper side of the head assembly 54a through the jacket communication paths 112 and 112. (Not shown) to cool the head assembly portion 54a of the continuous wall portion 54 therebetween. In addition, the cylinder head fastening bosses 55 and 55 positioned on the left and right of the head assembly portion 54a of the continuous wall portion 54 have the same shape as the conventional example (1) and the cylinder jackets 58 and 58. It is located outside of.

Although the prior art example (2) cuts off the lower part of the cylinder which forms each jacket communication path 112, and forms the coolant introduction part 113, since the coolant of the said coolant introduction part 113 is small, a large quantity Cooling water cannot be introduced into the cooling water 115 smoothly, and the head assembly portion 54a of the continuous wall portion 54 cannot be cooled strongly.

In addition, since the cooling water passage 115 is flat and lengthwise, the circumferential thickness of the continuous oil wall portion 54 cannot be made sufficiently thin in the same manner as in the conventional example (1), so that the interval between the cylinder bores 53a is reduced. In addition, it is difficult to further increase the engine output by narrowing the volume and increasing the displacement.

In addition, since the right and left cylinder head fastening bosses 55 and 55 are located outside the cylinder jackets 58 and 58, the space between the left and right head bolts 56 and 56 is the same as in the conventional example (1). There is a difficulty in that the cylinder 53 cannot be tightened uniformly and strongly along the circumferential direction.

12 (A), (B) and (C) show a conventional example (3), and FIG. 12 (A) is a longitudinal sectional view of a main part of a multi-cylinder cylinder. FIG. 12 (B) is a cross-sectional view in the direction of arrow B-B in FIG. 12 (A), and FIG. 12 (C) is a perspective view of the channel forming member injected into the continuous six wall portion of the multi-cylinder cylinder.

This conventional example (3) also comprises a plurality of cylinders 53 in the cylinder block 51 in front and rear, and the adjacent cylinders 53 and 53 are continuous in the continuous oil wall portion 54 to constitute the multi-cylinder cylinder 52. The cylinder jacket 58 is formed so as to surround the multi-cylinder cylinder 52, and the channel forming member 110 is injected into the continuous six wall portion 54.

The channel forming member 110 has a pair of left and right jacket communication paths 112 and 112 and lower portions of the jacket communication paths 112 and 112, as shown in FIGS. 12A, 12B, and 12C. The left and right pairs of coolant inlets 113 and 113, which are open toward the respective cylinder jackets 58 and 58, and the left and right pairs of coolant which communicate with each jacket communication path 112 and the coolant inlet 113, respectively. The cooling water passage 115 is provided with a furnace 113, which is flat when viewed from the front, longitudinally long when viewed from the longitudinal side, and is formed in a bag shape. The cooling water in the cylinder jacket 8 is formed by cooling water. The inlet 113, the cooling water passage 115, and the jacket communication passage 112 flow out to the head jacket in the meantime, and are configured to cool the head assembly portion 54a of the continuous wall portion 54 during this time.

The channel forming member 110 is formed by forming two metal plate-shaped bodies 110a and 110a by molding, and the non-cavity portions 111 and 111 of the horizontal H-shape are fixed to each other. The junction part 117 formed in the outer side of the jacket and communication paths 112 and 112 is not stuck only by overlapping. In addition, since the shape of the said junction part 117 differs in the front-and-back two metal plate-shaped objects 110a and 110a, it is not symmetrical.

In the said conventional example (3), since the cooling water path 115 becomes flat and lengthwise, since the circumferential thickness of the said continuous meat wall part 54 cannot be made thin enough in the same shape as the conventional example (1), a cylinder It is difficult to narrow the spacing of the bores 53a and increase the displacement so as to further increase the engine output.

In addition, in the said prior art example (3). Since the inlet interval of the coolant inlet 113 is small in the same manner as in the conventional example (2), a large amount of coolant cannot be smoothly introduced into the coolant passage 115.

As a result, in any of the prior art examples (1) to (3), the bore size of the cylinder bore 53a cannot be narrowed because none of the conventional thicknesses of the continuous oil wall portion 54 can be made sufficiently thin. . Also. There is a difficulty in that the head assembly portion 54a of the continuous oil wall portion 54 cannot be cooled strongly. In this manner, the head assembly portion 54a of the continuous oil wall portion 54 cannot be strongly cooled, and if the heat dissipation ability is lowered, output of the engine cannot be achieved.

That is, the piston ring is cooled through the cylinder wall, but the top ring is not mounted with a certain distance from the front of the piston, especially in view of preventing the piston ring from sticking out when the heat dissipation ability of the head assembly 54a is reduced. Can't. This means that a ring-shaped dead space does not contribute to combustion on the outer circumference of the piston peak. For this reason, it is not possible to improve the air utilization rate, and furthermore, to increase the output of the engine.

Further, in diesel engines, the compression ratio is high and a gas seal pressure of approximately 900 Kg / cm 2 or more is required. However, in any of the prior art examples (1) to (3), the bosses 55 for fastening the cylinder head are any. And 55) are large, and the cylinder 53 cannot be uniformly and strongly fastened along the circumferential direction, so that the gas chamber pressure cannot be sufficiently increased when applied to a diesel engine.

In particular, in recent years, it has been requested to promote smaller and lighter cargoes and to achieve higher output of the engine. However, the above-described conventional examples (1) to (3) cannot satisfy their requests sufficiently because of the above-mentioned difficulties. . The present invention has been considered in view of such circumstances,

a) Since the circumferential thickness of the continuous six-wall portion can be reduced to an extreme, the multi-cylinder engine further improves the output of the engine by miniaturizing and reducing the weight.

b) The technical problem is to improve the air utilization rate and improve the output of the engine by cooling the head assembly of the continuous wall part more powerfully and positioning the top ring upward.

As for the cooling apparatus of the multi-cylinder cylinder which concerns on this invention, as shown, for example in FIG. 1 (A), (B). It has the following basic configuration.

A plurality of cylinders 3 are placed in the cylinder block 1 before and after, and adjacent cylinders 3 and 3 are continuous in the continuous wall portion 4 to form a multi-cylinder cylinder 2, and The cylinder jacket 8 is formed so as to surround the cylinder cylinder 2, and the channel forming member 10 is injected into the continuous oil wall portion 4 to form the cooling water in the cylinder jacket 8.8. Through the cooling water passage 15 formed in the member 10 and the jacket communication passages 12 and 12 in order to flow out to the head jacket 22 located above the head assembly portion 4a of the continuous oil wall portion 4. To be configured.

MEANS TO SOLVE THE PROBLEM This invention is equipped with the following characteristic structures in order to achieve the said technical subject.

In the multi-cylinder cylinder cooling device having the above basic configuration, the channel forming member 10 is a pair of longitudinal left and right jackets communicating the cylinder jackets 8 and 8 and the head jacket 22 in the cylinder block 1. With communication paths (12, 12). A plurality of upper and lower stage cooling water passages 15 communicating with the jacket communication passages 12 and 12, and a plurality of stages of non-joint portions 11 formed alternately with the plurality of stage cooling water passages 15, are provided.

In the present invention, the non-joint portion 11 formed by the upper and lower abdominal means of the channel forming member 10 is. It functions as a rib which mechanically reinforces the continuous wall part 4. As a result, the cooling water passage 15 formed alternately with the non-joint portion 11 as the upper and lower abdominal means increases the mechanical strength at the other end compared with the flat and long cooling water passage 115 of the conventional example. Thereby, in the hole processing of the cylinder bore 3a. There is no fear of partial distortion.

In addition, the non-cavity portion 11 formed by the upper and lower abdominal means mechanically reinforces the continuous wall portion 4, thereby making it possible to thin the channel forming member 10 to the maximum, and further, to extend the continuous meat wall portion 4 to the extreme. I can thin it. Thereby, the circumferential thickness of the said continuous oil wall part 4 can be formed thinner than the conventional example, and a pitch can be made small between cylinder bores. Alternatively, by increasing the diameter of the cylinder bore, it is possible to increase the displacement and further the output.

In addition, the coolant in the cylinder jackets 8 and 8 flows smoothly along the outer circumferential surface 3a of the cylinder, and is located at the upper side of the continuous wall portion 4 through the coolant passage 15 and the jacket communication passage 12. Exit to (22). In the meantime, most of the cooling water flows through the cooling water passage 15 in the upper half to strongly cool the head assembly 4a. And the piston ring is strongly cooled through the cylinder wall. This can improve the output of the engine as described below.

a) The piston ring can be strongly cooled through the cylinder wall, so that the top ring is as close as possible to the piston face, and the ring-shaped dead space that does not contribute to the combustion of the piston apex is extremely small to improve air utilization. Can be planned. In addition, this can eliminate deadlock of the top ring due to carbonization of unburned portions of fuel and lubricating oil.

b) As the top ring is as close to the front of the piston as possible, the position of the piston pin as close to the front of the piston as possible, lengthening the turning index of the crankshaft by that part, and the physique of the cold start indicator engine By not changing (height), the piston stroke, and further, the displacement of the exhaust gas can be achieved. As a result, it is possible to reduce the size of the multi-cylinder engine and increase the output of the engine.

c) On the contrary, when the piston stroke is not changed inversely, the cold start indicator can be set as long as the position of the piston pin is close to the front of the piston, so that the lateral pressure of the piston can be reduced, and consequently, the friction loss can be reduced. It is planned.

d) In addition, since the head assembly can be strongly cooled, the circumferential thickness of the head assembly can be made thin, so that the diameter of the cylinder bore can be increased as much as the thickness of the head assembly becomes thin. have.

Description of Examples

EMBODIMENT OF THE INVENTION Hereinafter, 1st Embodiment of this invention is described based on drawing.

3 is a longitudinal sectional view of an essential part of a vertical multicylinder engine injecting a channel forming member according to a first embodiment of the present invention.

As shown in FIG. 3, the vertical multi-cylinder engine E fixes the cylinder head 20 with the head bolt 6 on the cylinder block 1 in which the crankcase is integrally formed. The cylinder jacket 8 formed in the cylinder head 8 and the head jacket 22 formed in the cylinder head 20 are communicated with a plurality of jacket communication holes 24 formed in portions other than the continuous wall portion 4, so that the cylinder block ( It is comprised so that the cylinder head 20 may be cooled by the cooling water which cooled 1).

In the multi-cylinder cylinder cooling device according to the present invention, as shown in FIGS. 1A, 3B, and 3, a cylinder adjacent to a plurality of cylinders 3 is provided in the cylinder block 1 in front and rear. The cylinder jacket 8 is formed so that (3, 3) is continued by the continuous wall part 4, and the multi cylinder cylinder 2 is comprised and the said multi cylinder cylinder 2 is enclosed. The channel forming member 1 to be described later is injected into the continuous wall portion 4.

Hereinafter, the feature configuration of the first embodiment will be described.

As shown in Figs. 2 (A), (B) and (C), the channel forming member 10 overlaps the press-formed two metal plate-like bodies 10a and 10a so as to face each other and mutually contact portions. The seam is welded and is integrally formed. Thereby, it can manufacture easily so that the two metal plate-shaped objects 10a and 10a shape | molded in the same shape can adhere to each other.

The channel forming member 10 has a pair of jacket communication paths 12 and 12 in the longitudinal direction communicating the cylinder jacket 8.8 and the head jacket 22 in the cylinder block 1 with the jacket. A pair of upper and lower cooling water passages 15 communicating with the furnaces 12 and 12 and a plurality of stages of non-joint portions 11 alternately formed with the cooling water passages 15 of the plurality of stages are provided. The lower part of the furnace 12, 12 is formed as a pair of cooling water introduction parts 13 and 13 which open toward each cylinder jacket 8 and 8, and a large amount of cooling water introduced in the cooling water introduction parts 13 and 13, At the same time as the cooling water passage 15, the cooling water passage 15 flows out to the head jacket 22 located above the head assembly portion 40 through the jacket communication passages 12 and 12.

As in the above embodiment, when the non-joint portion 11 and the cooling water passage 15 are alternately formed in the upper and lower plural stages, the non-cavity 11 formed in the upper and lower plural stages mechanically forms the continuous ground wall portion 4 mechanically. It functions as a rib to reinforce, and the continuous wall part 4 at the time of machining a cylinder bore and at the time of engine operation compared with the case where the cooling water path 15 like the conventional example (1) was formed long and flat when viewed from the longitudinal side surface. There is an advantage in that it can be strong against the pressing force acting on.

As a result, the cooling water passage 15 formed of the upper and lower abdominal means alternately with the non-joint portion 11 is. Compared with the flat and long cooling water path 115 of the prior art example, the mechanical strength increases with a clearance. Thereby, there is no possibility that partial distortion will occur in the hole processing of the cylinder bore 3a.

In addition, the non-cavity portion 11 formed in the upper and lower plural stages mechanically reinforces the continuous oil wall portion 4, whereby the channel forming member 10 can be made extremely thin, and further, the continuous oil wall portion 4 is limited to the limit. Eggplant can be thinned. Thereby, the circumferential thickness of the said continuous oil wall part 4 can be formed thinner than before, and the pitch between cylinder bores can be made small. Alternatively, the diameter of the cylinder bore can be increased, so that the displacement of the cylinder can be increased, and thus the output can be increased.

The left and right pairs of cylinder head fastening bosses 5 and 5 are formed in succession with the left and right sides of the head assembly 4a, and the arrangement of the head bolts 6 and 6 is narrowed so as to be narrowed. The cylinder 3 is configured to fasten uniformly and strongly along the circumferential direction. In addition, this invention is not limited to this, The upper and lower walls of the cylinder block 1 are formed by forming a pair of left and right pairs of cylinder head fastening bosses 5 and 5 continuously with the left and right both sides of the head assembly 4A. There is an advantage in that a large amount of cooling water can be circulated by increasing the hole diameter of the jacket communication hole 23 and the pair of jacket communication paths 12 and 12 drilled in the hole.

The pair of jacket communication paths 12 and 12 are located inside the bosses 5 and 5, and the jacket communication holes 23 are formed in the upper wall of the cylinder block 1 and the lower wall of the cylinder head 20. ) In communication with In addition, the dimension d of the left and right of the cooling water path 15 is. As shown in FIG. 1 (A), (B), it is set smaller than the left-right dimension D of the said continuous meat wall part 4. As shown to FIG. As a result, the inner opening gap d of the pair of jacket communication paths 12 and 12 is set smaller than the left and right dimensions D of the continuous wall portion 4. therefore. As the inner opening gap d of the jacket communication paths 12 and 12 is narrowed, the disposition space of the left and right head bolts 6 and 6 can be narrowed, and the head bolt 6 around the cylinder 3 can be narrowed. Since the number of can be increased, the cylinder 3 can be tightened more uniformly and strongly along the lifting direction. As a result, the gas seal pressure can be increased.

In addition, the left and right pairs of coolant introduction parts 13 and 13 are provided with a pair of front and rear coolant guide plates 14 and 14 protruding from the left and right sides, respectively, along the outer peripheral surfaces 3a and 3a of the cylinders 3 and 3 adjacent to the front and rear. It is wide open. Since the opening of the coolant introduction section 13.13 is largely formed by the above configuration, the coolant passage 15 and the jacket from the coolant introduction sections 13 and 13 which are open toward the cylinder jackets 8 and 8 with a large amount of coolant. A large amount flows into the communication path 12, and exits through the jacket communication paths 12 and 12 to the head jacket 22 located above the continuous six wall portion 4. In the meantime, a large amount of cooling water flows through the cooling water passage 15 and the jacket communication passages 12 and 12 in the upper half to strongly cool the head assembly 4a. As a result, the engine can increase its displacement and, furthermore, its output.

In other words, by cooling the head assembly 4a strongly, the piston ring can be cooled strongly through the cylinder wall, so that the top ring is as close as possible to the front of the piston, and does not contribute to the combustion of the outer peripheral edge of the piston. The ring-shaped dead space can be extremely small to improve the air utilization rate. In addition, this can eliminate the deadlock of the top ring due to carbonization of the unburned part lubricant of the fuel.

In addition, as the top ring is as close to the front of the piston as possible, the position of the piston pin can be as close to the front of the piston as possible, so that the turning dimension of the crankshaft can be increased by that, and the cold start indicator engine does not change the physique. It is possible to reduce the size relatively, increase the piston stroke, and increase the displacement. In addition, since the head assembly portion 4a can be strongly cooled, the diameter of the cylinder bore can be increased, so that the displacement of the exhaust gas can be improved. In addition, the present invention can also be applied to a multi-cylinder engine equipped with a turbo charger, so that the size and size of the engine can be relatively high.

4 (A), (B), and (C) show a channel forming member frame according to the second embodiment of the present invention, and FIGS. 5 (A) and (B) show a cylinder block injecting the channel forming member. It shows the main part of.

As shown in the figure, the channel forming member 10 has the same shape as that of the first embodiment, and overlaps the two metal plate-like bodies 10a and 10a formed in the front-back symmetry by press molding so as to overlap each other. The end joints 17 and 17 formed by protruding in the longitudinal direction to the outer ends of the formed non-joint parts 11 and the left and right jacket communication paths 12. 12 are deeply welded, and are integrally formed. Hereinafter, the second embodiment will be described with respect to the differences from the first embodiment, and overlapping descriptions of common structures will be omitted.

In this embodiment, the non-cavity portion 11 and the cooling water passage 15 are alternately formed by the upper and lower abdomen, but as shown in FIGS. 4A and 4B, the cooling water passage 15 is planar. When viewed, the wedge-shaped cavity 15a is symmetrically configured so that its tip faces the center.

That is, the circumferential thickness of the continuous meat wall part 4 is the thinnest at the center part and thickest at the left and right ends, but is corresponding to the circumferential thickness of the continuous meat wall part 4 in the shape of a wedge when the cooling water passage 15 is viewed in plan view. The channel forming member 10 can be thinned to the maximum by forming the left and right symmetrical so that the tip is directed toward the center, and further, the continuous oil wall portion 4 can be thinned to the maximum. Thereby, the circumferential thickness of the said continuous oil wall part 4 can be formed thinner than the conventional example, and the pitch between cylinder bores can be made small. Alternatively, by increasing the diameter of the cylinder bore, it is possible to increase the displacement and further the output.

In addition, in the pair of left and right angular cooling water channels 15, as shown in FIG. 4 (A), the upper edges 15h are formed in an upward gradient to the outside in the left and right directions. That is, even when cooling water is boiled in each cooling water passage 15 to generate steam, the water vapor moves upward along the upper edge 15b of the respective cooling water passages 15 formed in the upper gradient, and the jacket communication passage 12 Run through the head jacket (22). As a result, the cooling performance is maintained high.

In addition, one outer joint part 17 of the outer edge of the jacket communication paths 12 and 12 is between the one cylinder 3 and the cylinder head fastening boss part 5, and the other outer joint part 17 Between the other cylinder 3 and the cylinder head fastening boss part 5, they are inject | poured by shifting to the joint part of one cylinder and the other cylinder 3, 3, respectively. That is, since the interval between the left and right cylinder head fastening bolts 6 and 6 is constant, if the joint 17 is overlapped with the outer side of the left and right jacket communication paths 12 and 12 as in the conventional example, the corresponding jacket communication path 12 The cross-sectional area of the real passage of 적 becomes small. Therefore, as described above, by aligning the outer edge joining portions 17 and 17 to the joining of the cylinders 3 and 3 on one side and the other, the cross section of the actual passage of the jacket communication passage 12 can be increased.

As shown in FIG. 4B, a pair of jacket communication paths 12. 12 are located inside the bosses 5, 5, and at the same time, as shown in FIG. It is in communication with the jacket communicating hole 23 drilled in the upper wall of the block 1 and the lower wall of the cylinder head 20. In addition, as shown in FIG. 4 (A), the upper end portion of the jacket communication path 12 has a slightly higher elongation than the non-cavity portion 11 of the upper edge. This is intended to fold and bind the middle thread 12b for forming the jacket communication hole 23 by setting the jacket communication hole 23 of the upper wall of the cylinder block 1 relatively short. It is.

Reference numeral 16 in Fig. 4A is a hole for connecting the front and rear wall of the continuous wall portion 4. The non-cavity part 11 of this invention is not limited to having this front and back ground wall connection hole 16. In the case of having the front and rear wall connecting holes 16, there is an advantage that the pressing force acting on the continuous wall portion 4 at the time of machining the cylinder bore and at the time of engine operation can be more strongly countered. In addition, the shape of the front and back ground wall connection hole 16 is mentioned later. 6A and 6B show a channel forming member according to a third embodiment of the present invention, and FIG. 6A is a perspective view of the channel forming member, and FIG. 6B shows a channel forming member. This is a longitudinal front view of.

In this embodiment, as shown, the non-cavity portion 11 is formed in a V shape, and the upper edge 15b and the lower edge 15c of each of the wedge-shaped cooling water passages 15 on the left and right are upper and lower outward in the left and right directions. It is formed by a ship, and the difference is comprised in the same shape as the said 2nd Example (FIG. 4 (A)). That is, even when the cooling water is boiled in each of the cooling water passages 15 to generate steam, the water vapor moves upward along the upper edge 15b of each of the cooling water passages 15 formed in the upper gradient to open the jacket communication passage 12. Run through the head jacket (22). In addition, since at least the upper edge 15b of each of the left and right pairs of the cooling channels 15 is formed in an upper gradient to the outside in the left and right directions, the upper edge 15c of each of the cooling channels 15 is upward and downward in the left and right directions. Formation or not is freedom.

7A and 7B show a channel forming member according to a fourth embodiment of the present invention. 7A is a perspective view of the channel forming member, and FIG. 7B is a front view of the channel forming member.

In this embodiment. As shown. The outer joint portions 17, 17 formed by pressing two metal plate upper bodies 10a. 10a formed symmetrically by press molding so as to face each other and protruding outwardly in the outer edges of the left and right jacket communication paths 12, 12. ) Weld together and are integrally comprised. Thereby, it can be manufactured simply and inexpensively only by fixing the outer edge joint parts 17 and 17 of the two metal plate-shaped objects 10a and 10a shape | molded in the same shape to each other. Moreover, it does not interfere even if it substitutes with the said core welding and arc spot welding.

In this embodiment, as shown in the drawing, the front and rear wall connecting holes 16 are formed in the non-joint part 11 to connect the front and rear wall of the continuous wall part 4 to each other. It is comprised in the form similar to 2nd Example (FIG. 4 (A)).

That is, since the non-cavity portion 11 has the front and rear wall connecting holes 16 formed of long holes, the non-cavity portion 11 is more powerful against the pressing force acting on the continuous wall portion 4 during machining of the cylinder bore and during engine operation. The advantage is that you can fight back.

Further, the non-joint portion 11 formed by the upper and lower abdominal means functions as a rib for mechanically reinforcing the continuous six-wall part 4, so that the cooling water passage 15 formed by the upper and lower abdominal means alternately with the non-cavity part 11 is a conventional example. Compared to the flat, long cooling water passage 15, the mechanical strength increases at the other end. This eliminates the possibility of partial distortion in the drilling of the cylinder bore 3a.

In addition, since the upper edge 15b of the cooling water passage 15 is formed in an upward gradient to the outside in the left and right directions, the cooling performance is maintained high. That is, even when the cooling water is boiled in the cooling water passage 15 to generate steam, the water vapor moves upward along the upper edge 15b of each of the cooling water passages 15 formed in the upper gradient, and passes through the jacket communication passage 12. Run away with the head jacket (22). As a result, the cooling performance is maintained high.

8 (A), (B) and 9 (A), (B) are front views showing a modification of the channel forming member according to the fourth embodiment, and FIG. The modification (1) of the member, FIG. 8 (B) shows the modification (2) of the channel forming member, and FIG. 9 (A) shows the modification (3) and FIG. 9 (B) of the channel forming member. Denotes a modification (4) of the channel forming member.

As shown in FIG. 8 (A), the modified example (1) has non-joint portions of the outer joint portions 17 and 17 formed by protruding outwardly on the outer edges of the left and right jacket communication paths 12 and 12, respectively. (11) The cores are welded together and fixed together. The difference is comprised in the shape like FIG. 7 (A).

As shown in FIG. 8 (B), the modification (2) has nostrils between the outer joint portions 17 and 17 formed by protruding outwardly on the outer ends of the left and right jacket communication paths 12 and 12, respectively. The eastern parts 11 and 11 are welded together, and the non-cavity parts 11 and 11 formed by the upper and lower abdominal means are arc-spot welded, and are integrally fixed. In addition, the front and rear wall connecting holes 1b formed in each non-cavity portion 11 are formed by drilling a plurality of annular holes at a predetermined pitch, and the other point is configured as shown in Fig. 7A. As described above, by arc spot welding the non-joint parts 11 and 11 and fixing them integrally, it is possible to prevent scanning from invading between the non-joint parts 11 and 11 and to form a gap.

That is, when the channel forming member 10 is injected into the head assembly portion 4a of the continuous wall portion 4, the jacket communication path 12 and the cavity 15 of the channel forming member 10 are preceded. When the injection is press-fitted by a high-pressure air and filled, but the non-joint parts 11 and 11 do not adhere to each other, a scan is made to penetrate between the non-joint parts 11 and 11 so that a gap is formed. There is a problem that the thickness of 10) becomes large, but by welding the non-joint portions 11 and 11 together and integrally fixing these problems, it is possible to solve such a problem and maintain the exact thickness dimension of the channel forming member 10.

In the modification (3), as shown in FIG. 9A, the non-joint part 11 of the upper and lower abdomen means is connected with the longitudinal non-joint part 11b at the center part. In addition, the front and rear wall connecting holes 16 formed in each non-cavity part 11 are formed in the length hole, The other point is comprised in the shape like FIG. 7 (A). In addition, the left and right pairs of wedge-shaped cooling water passages 15 are formed in a bag shape in which the center part is closed by being divided in the longitudinal non-cavity portion 11B, but the cooling water is a pair of bags by the cooling water introduction portions 13 and 13. A large amount flows into the shape cooling water path 15 and the jacket communication path 12, and exits through the jacket communication paths 12 and 12 to the head jacket 22 located above the continuous wall portion 4.

As shown in FIG. 9 (B), the modified example 4 includes non-joint portions of the outer joint portions 17 and 17 formed by protruding outwardly on the outer ends of the left and right jacket communication paths 12 and 12. (11) We fix each other by deep welding. In addition, the front and rear wall connecting holes 16 formed in each non-cavity part 11 are formed through a single annular hole, and the difference is comprised in the shape like FIG. 7 (A).

This invention is not limited to the said Example, For example, various changes can be implemented by combining the following elements (a)-(j) suitably.

(a) the cooling water passage 15 formed in the shape of a bag with the middle part closed;

(b) Left and right pairs of coolant introduction portions (13.13) formed in the lower portion of the left and right pair of jacket communication paths (12, 12) and opened toward the respective cylinder jackets (8, 8).

(c) Front and rear wall connecting holes 16 formed in each non-joint portion 11 formed by upper and lower abdominal means;

(d) Cooling water passage 15 composed of symmetrical sides of the wedge shaped cavity 15a in plan view, with its tip facing the center.

(e) Cooling water passage 15 formed with an upper gradient of the upper end 15b in left and right directions outward

(f) A pair of left and right cylinder head fastening bosses 5 and 5 are formed on the left and right sides of the head assembly portion 4a of the continuous oil wall portion 4 to form the jacket communication paths 12 and 12. It is located inside the pair of cylinder head fastening bosses 5 and 5.

(g) The channel forming member 10 integrally molded by, e.g., precision casting, instead of forming the channel forming member 10 by opposing and fixing the two metal plate-like bodies 10a.

(h) formed by protruding outwardly from the non-joint portions 11 and 11 of the two metal plate-like bodies 10a and 10a constituting the channel forming member and the outer ends of the jacket communication paths 12 and 12 on the left and right sides. The outer joints 17.17 fixed to each other,

(i) The inner opening gap d of the pair of jacket communication paths 12 and 12 is set smaller than the left and right dimensions D of the continuous oil wall part 4.

(j) One outer edge joining portion 17 is the other outer edge joining portion 17 between one cylinder 3 and the cylinder head fastening boss portion 6 is the other cylinder 3 and the cylinder. Between the head fastening boss part 5, it arrange | positioned and inject | poured into one set and the other cylinder 3 set, respectively.

1 (A) and (B) show a cylinder block injecting a channel forming member according to a first embodiment of the present invention,

1 (A) is a longitudinal sectional view of the main part of the cylinder block in which the channel forming member is injected;

1B is a partial plan view of the cylinder block.

2 (A), (B) and (C) show a channel forming member according to the first embodiment of the present invention,

2 (A) is a perspective view of the channel forming member,

2B is a longitudinal sectional view seen from the arrow direction of the B-B line in FIG. 2A,

FIG. 2C is a cross-sectional plan view of the arrow direction of the C-C line in FIG. 2A.

3 is a longitudinal sectional view of an essential part of a vertical multicylinder engine injecting a channel forming member according to the first embodiment.

4A, 4B, and 4C show a channel forming member according to a second embodiment of the present invention.

4 (A) is a perspective view of the channel forming member,

4 (B) is a plan view showing a half of the right side of the channel forming member broken;

4 (C) is a longitudinal cross-sectional view seen from the arrow direction of the C-C line in FIG. 4 (A) and FIG. 4 (B).

5 (A) and 5 (B) show main parts of the cylinder block into which the channel forming member according to the second embodiment is injected;

5 (A) is a partial longitudinal sectional view of the cylinder block,

5B is a partial plan view of the cylinder block.

6A and 6B show a channel forming member according to a third embodiment of the present invention.

6 (A) is a perspective view of the channel forming member,

6B is a longitudinal sectional front view of the channel forming member.

7A and 7B show a channel forming member according to a fourth embodiment of the present invention.

7 (A) is a perspective view of the channel forming member,

7B is a front view of the channel forming member.

8 (A), (B) and 9 (A), (B) are front views showing a modification of the channel forming member according to the fourth embodiment of the present invention.

8 (A) shows a variation (1) of the channel forming member,

8B is a modified example (2) of the channel forming member;

9 (A) shows a modification (3) of the channel forming member,

9B shows a modification 4 of the channel forming member.

(A), (B), (C) of FIG. 10 shows the prior art example (1),

10A is a longitudinal sectional view of an essential part of a multi-cylinder cylinder of a vertical engine,

FIG. 10B is a cross-sectional plan view taken along line B-B in FIG. 10A in the direction of the arrow;

10C is a perspective view of the channel forming member.

5 (A) and 5 (B) show main parts of the cylinder block into which the channel forming member according to the second embodiment is injected;

5 (A) is a partial longitudinal sectional view of the cylinder block,

5B is a partial plan view of the cylinder block.

6A and 6B show a channel forming member according to a third embodiment of the present invention.

6 (A) is a perspective view of the channel forming member,

6B is a longitudinal sectional front view of the channel forming member.

7A and 7B show a channel forming member according to a fourth embodiment of the present invention.

7 (A) is a perspective view of the channel forming member,

7B is a front view of the channel forming member.

8 (A), (B) and 9 (A), (B) are front views showing a modification of the channel forming member according to the fourth embodiment of the present invention.

8 (A) shows a variation (1) of the channel forming member,

8B is a modified example (2) of the channel forming member;

9 (A) shows a modification (3) of the channel forming member,

9B shows a modification 4 of the channel forming member.

(A), (B), (C) of FIG. 10 shows the prior art example (1),

10A is a longitudinal sectional view of an essential part of a multi-cylinder cylinder of a vertical engine,

FIG. 10B is a cross-sectional plan view taken along line B-B in FIG. 10A in the direction of the arrow;

10C is a perspective view of the channel forming member.

11 (A), (B), and (C) show a conventional example (2)

11A is a longitudinal sectional view of an essential part of a multi-cylinder cylinder of a vertical engine,

(B) is a transverse plan view seen from the arrow direction of the B-B line in FIG. 11 (A),

11C is a perspective view of the channel forming member.

12 (A), (B) and (C) show a conventional example (3),

12A is a longitudinal sectional view of an essential part of a multi-cylinder cylinder of a vertical engine,

12B is a transverse plan view seen from the direction of the arrow B-B in FIG. 11A,

12C is a perspective view of the channel forming member.

Claims (8)

Injecting the channel forming member 10 into the head assembly portion 4a of the continuous six wall portion 4 between the adjacent bores 3a and 3a of the multi-cylinder cylinder block 1, Cooling water in the cylinder jackets (8, 8) located on the left and right of the continuous wall portion (4) flows out through the water channel forming member (10) to the head jacket (22) located above the head assembly (4a). In the cooling device of a multi-cylinder cylinder configured to The channel forming member 10 is located under the left and right jacket communication paths 12 and 12 extending up and down to communicate the left and right cylinder jackets 8 and 8 and the head jacket 22, and each cylinder jacket 8 A plurality of horizontally arranged in the upper and lower ends communicating the pair of left and right coolant introduction portions 13 and 13 and the left and right jacket communication passages 12 and 12 and the right and left coolant introduction portions 13 and 13 communicating with each other. Characterized by comprising a cooling water passage (15) and a plurality of non-joint portions (11) which are rolled up mutually with each cooling water passage (15) and separate adjacent ones of the cooling water passage (15) up and down. Chiller of multi-cylinder cylinder, In the cooling device according to claim 1, A pair of left and right pairs of cylinder head fastening bosses 5 and 5 are formed in succession to the left and right sides of the head assembly portion 4a of the continuous six wall portion 4, and the coolant introduction portions 13 and 13 are connected to the cylinder. The front and rear cylinders are arranged in close proximity to the lower surfaces of the head fastening bosses 5 and 5, and the openings are largely opened up and down. A multi-cylinder cylinder cooling device, characterized in that it is wide open back and forth by mating to outer peripheral surfaces (3a, 3a). In the cooling device of Claim 1 or 2, Cooling apparatus for a multi-cylinder cylinder, characterized in that at least one or more front and rear wall connecting holes (16) of the continuous ground wall portion (4) is formed in each non-joint portion (11). In the cooling device of Claim 1 or 2, Each of the cooling water passages 15 is a multi-cylinder cylinder, characterized in that the cavities 15a of the wedge-shaped view in plan view are configured symmetrically so that their ends face toward the center of the continuous six wall portions 4. Chiller. In the cooling device of Claim 1 or 2, The cooling device of the multi-cylinder cylinder which formed each cooling water path 15 by the gradient which raises the upper edge 15b to the left-right direction outside at least. In the cooling device of Claim 1 or 2, The inner opening gap d of the pair of jacket communication paths 12 and 12 is set smaller than the left and right dimensions D of the continuous wall part 4. Cooling apparatus for a multi-cylinder cylinder characterized in that. In the cooling device of Claim 1 or 2, The channel forming member 10 is formed in front and rear symmetry by molding two metal plate-shaped bodies 10a and 10a, and the plurality of upper and lower non-cavities 11 and 11 and the left and right jacket communication paths 12, Cooling device for a multi-cylinder cylinder, characterized in that the outer joint portion (17, 17) formed by protruding in the longitudinal direction on the outer edge of 12) is fixed to each other. In the cooling device according to claim 7, A pair of left and right pairs of cylinder head fastening bosses 5 and 5 are formed continuously on both left and right sides of the head assembly 4a of the continuous inner wall 4, and the outer edge joint 17 in one direction is formed on one side. Between the cylinder 3 and the corresponding cylinder head fastening boss portion 5, the outer joint 17 in the other direction is the cylinder 3 in the other direction and the corresponding boss for fastening the cylinder head in the other direction ( 5) A multi-cylinder cylinder cooling device, characterized in that it is configured to be injected into a set of cylinders (3) in one direction and the other direction, respectively.