Water-cooled type internal combustion engine

Abstract: A water-cooled type internal combustion engine includes a cylinder (13 2 ) provided in a cylinder block (11) of an engine body (E) and having a piston (12) slidably received therein, and a cooling water passageway (14) defined in the engine body and including a cooling water portion (14a) surrounding the cylinder. In the water-cooled type internal combustion engine, a through-bore (17 1 ) is provided at that portion of an outer wall (11b) of the engine body which faces the cooling water passageway, a vibration absorbing means (16 1 ) is mounted to the outer wall surface of the engine body to close the through-bore. The vibration absorbing means includes a resilient membrane (18 1 ) which is disposed so that its peripheral edge does not protrude from an inner surface of the outer wall into the cooling water passageway, and which has one surface facing the cooling water passageway and the other surface facing a space area (20 1 ) .

Description: The present invention relates to a water-cooled type internal combustion engine including a cylinder provided in a cylinder block of an engine body and having a piston slidably received therein, and a cooling water passageway defined in the engine body and surrounding the cylinder. A problem in such water-cooled type internal combustion engines can be the production of a piston slap sound by the collision of the piston against an inner surface of the cylinder. In reducing the piston slap sound in the cylinder block structure in the water-cooled type internal combustion engine, at least the five following techniques have been conventionally employed: (1) a technique in which the wall thickness of the cylinder is increased to suppress the amplitude of a vibration to a small level, and (2) a technique in which the wall thickness of an outer wall of the cylinder block is increased to suppress the amplitude of a vibration. Also known are structures designed to inhibit a vibration of the non-compressible cooling water existing in the cooling water passageway, including (3) a structure in which an expandable member such as a gas-encapsulated bellows is mounted in the outer wall of the cylinder block in such a manner that it is disposed in the cooling water passageway, as disclosed in Japanese Utility Model Application Laid-open No.57-101345, (4) a structure in which a sound shielding layer is provided in the cylinder block outside the cooling water passageway with a partition wall interposed therebetween, as disclosed in Japanese Utility Model Application Laid-open No.53-68814, and (5) a structure in which a sponge-like damper material covered with a metal plate is affixed to an inner surface of the outer wall of the cylinder block in the cooling water passageway, as disclosed in Japanese Patent Application Laid-open No.57-102539. However, in the techniques (1) and (2), the weight of the engine body is increased due to increases in wall thickness of the cylinder and the cylinder block. In the structure (3), the existence of the expandable member in the cooling water passageway causes the flow of the cooling water in the cooling water passageway to be hindered, bringing about a reduction in cooling performance, and also the spring characteristic of the expandable member is varied in accordance with a variation in internal pressure of a gas in the expandable member depending upon the temperature of the cooling water, thereby reducing the vibration damping effect by half during operation of the engine. In the structure (4), the cooling water passageway and the sound shielding layer are disposed with the partition wall interposed therebetween to provide a double structure and hence, this structure is complicated and difficult to manufacture, resulting in an increase in manufacture cost, and bringing about an increase in weight of the engine body. Further, in the structure (5), the presence of the damper material covered with the metal plate in the cooling water passageway causes the flow of the cooling water in the cooling water passageway to be hindered, bringing about a reduction in cooling performance. Accordingly, it is an object of a first aspect of the invention to provide a water-cooled type internal combustion engine, wherein the piston slap sound can be effectively reduced in a simple structure which causes no reduction in cooling performance and no significant increase in weight of the engine body. US-A-3889841 discloses a water-cooled type internal combustion engine comprising a cylinder provided in a cylinder block of an engine body and having a piston slidably received in the cylinder, and a cooling water passageway defined in the engine body and including a water passage portion surrounding the cylinder wherein said internal combustion engine further includes a through-bore provided at that portion of an outer wall of the engine body which faces the cooling water passageway, and means mounted to the outer wall surface of the engine body to close said through-bore, said means including a resilient membrane positioned adjacent said through-bore and having a first surface facing the cooling water passageway and a second surface facing outwardly of the engine block, and a housing covering said resilient membrane. In this disclosure, however, the membrane is used to allow for expansion when the cooling water freezes and there is no teaching concerning vibration absorption. It is known from GB 2134974A to provide a water-cooled type internal combustion engine comprising a cylinder provided in a cylinder block of an engine body and having a piston slidably received in the cylinder, and a cooling water passageway defined in the engine body and including a water passage portion surrounding the cylinder wherein said internal combustion engine further includes a through-bore provided at that portion of an outer wall of the engine body which faces the cooling water passageway. A vibration absorbing means is provided which may be in the form of a bubble-forming gas or gas mixture which is added to the coolant or mixed therewith, or may result as a consequence of adding compressible particles to the coolant, or by introducing elastic sachets into the coolant, or by spraying one or both inner sides of the engine casing with compressible damping layers, or by attaching compressible material to the walls. The present invention is characterized over the disclosure of US-A-3889841 in that said means is a vibration absorbing means and said housing forms a space area between said second surface and said housing, said space area being of a volume for effectively absorbing vibrations transmitted through the cooling water. In a preferred arrangement, a vibration produced as a result of the collision of the piston against an inner surface of the cylinder induces a vibration of the cooling water in the cooling water passageway. However, a variation in pressure of the cooling water is absorbed by the flexure of the resilient membrane having the one surface facing the cooling water passageway, thereby effectively reducing the vibrating force applied from the cooling water to the outer wall of the engine body to reduce the piston slap sound radiated from the engine body. Moreover, since the peripheral edge of the resilient membrane does not protrude from the outer wall of the engine body into the cooling water passageway, it is possible to avoid the hindrance by the resilient membrane of the flow of the cooling water in the cooling water passageway to the utmost, and to smooth the flow of the cooling water in the cooling water passage to maintain the cooling performance. In addition, the space area faced by the other surface of the resilient membrane cannot be surrounded by the cooling water passageway, and even if a variation in temperature of the cooling water is produced, the temperature of a gas in the space area is varied only in a small amount. Even if the space area is tightly closed, the variation in pressure in the space area can be suppressed to a very small level and hence, an excellent vibration absorbing effect can be obtained during operation of the engine. Further, since the vibration absorbing means is mounted to a portion of the outer wall surface of the engine body, it is possible to suppress the increase in weight of the engine body due to the mounting of the vibration absorbing means to a small level. According to preferred embodiments of the present invention, a plurality of the cylinders equal to three or more are disposed in parallel in the cylinder block, and the vibration absorbing means is mounted to the cylinder block at an intermediate location in a direction of the arrangement of the cylinders. In a multi-cylinder water-cooled type internal combustion engine including three or more cylinders, it has been confirmed by experiments made by the present inventors that the amplitude of the vibration of the cooling water is increased at the intermediate location in the direction of the arrangement of the cylinders. However, by the disposition of the vibration absorbing means at the location at which the vibration amplitude is larger, the piston slap sound can be more effectively reduced by a small number of vibration absorbing means. Some preferred embodiments of the invention will now be decsribed by way of example only and with reference to the accompanying drawings in which: Figs.1 to 5 illustrate a first embodiment of the present invention, wherein Fig. 1 is a perspective view of a cylinder block in a 4-cylinder water-cooled type internal combustion engine; Fig. 2 is an enlarged sectional view taken along the line 2-2 in Fig. 1; Fig. 3 is a view taken in the direction of the arrow 3 in Fig. 2; Fig. 4 is a diagram showing a mode of vibration of an outer wall surface of a cylinder block in the direction of the arrangement of cylinders; Fig. 5 is a diagram showing the acceleration characteristic with respect to the frequency in comparison with that in the prior art; Fig. 6 is a sectional view similar to Fig. 2, but illustrating a second embodiment; Fig. 7 is a sectional view similar to Fig. 2, but illustrating a third embodiment; Fig. 8 is a side view of a portion of a cylinder block in a fourth embodiment; Fig. 9 is a sectional plan view taken along the line 9-9 in Fig. 8; Fig. 10 is a side view of a cylinder block in a fifth embodiment; Fig. 11 is a sectional view similar to Fig. 2, but illustrating a sixth embodiment; and Fig. 12 is a cross-sectional plan view of a portion of an engine body in a seventh embodiment. A first embodiment of the present invention will now be described with reference to Figs.1 to 5. Referring first to Figs.1 and 2, an engine body E in a water-cooled type 4-cylinder internal combustion engine comprises a cylinder block 11 together with a cylinder head, an oil pan and the like (not shown). First, second, third and fourth cylinders 13 1 , 13 2 , 13 3 and 13 4 are provided in parallel in the cylinder block 11, and pistons 12 are slidably received in the first, second, third and fourth cylinders 13 1 , 13 2 , 13 3 and 13 4 , respectively. Each of the cylinders 13 1 , 13 2 , 13 3 and 13 4 is comprised of cylinder liner 15 formed in a cast-in manner on an inner wall 11a included in the cylinder block 11 in this embodiment, but may be comprised of an inner wall 11a having a ground inner surface rather than a liner. A cooling water passageway 14 is defined in the engine body E and includes a water passage portion 14a defined in the cylinder block 11 to commonly surround the cylinders 13 1 , 13 2 , 13 3 and 13 4 . A small gap is left between an outer surface of each of the pistons 12 and an inner surface of each of the cylinders 13 1 , 13 2 , 13 3 and 13 4 . When the piston 12 is vertically moved in each of the cylinders 13 1 , 13 2 , 13 3 and 13 4 , it collides against the inner surface of each of the cylinders 13 1 , 13 2 , 13 3 and 13 4 to vibrate each of the cylinders 13 1 , 13 2 , 13 3 and 13 4 , and such vibration is transmitted to the cooling water in the cooling water passageway 14. The cooling water is non-compressible and hence, a variation in pressure is produced even by such a slight vibration. A vibrating force produced by the variation in pressure of the cooling water is applied to an outer wall 11b of the cylinder block 11 facing the cooling water passageway 14, thereby vibrating the outer wall 11b to radiate a piston slap sound to the outside. Therefore, vibration absorbing means 16 1 for absorbing the vibration of the cooling water in the cooling water passageway 14 to inhibit the application of the vibrating force to the outer wall 11b of the cylinder block 11 to the utmost to reduce the piston slap sound are mounted to the outer wall 11b of the cylinder block 11 at locations corresponding to sleeve bore centers of the second and third cylinders 13 2 and 13 3 which lie in intermediate locations in the direction of the arrangement of the cylinders 13 1 , 13 2 , 13 3 and 13 4 . Threaded bores 17 1 as through-bores are provided in the outer wall 11b of the cylinder block 11 in correspondence to the vibration absorbing means 16 1 . The vibration absorbing means 16 1 includes a resilient membrane 18 1 having one surface facing the water passage portion 14a of the cooling water passageway 14, and a housing 19 1 which defines a space area 20 1 between the housing 19 1 and the other surface of the resilient membrane 18 1 . Referring also to Fig.3, the housing 19 1 is formed into a bottomed cylinder-like shape with its outer end closed by a metal material having a substantial rigidity. Formed on an outer surface of the housing 19 1 are, in sequence from its inner end, an externally threaded portion 21 which is threadedly inserted into the threaded bore 17 1 , an engage collar portion 22 which protrudes outwards from the externally threaded portion 21, and an engaging portion 23 which is formed, for example, into a substantially hexagonal shape for engagement of a rotative operating tool such as a wrench. The distance from the inner end of the housing 19 1 to the engage collar portion 22 is set such that when the externally threaded portion 21 is threadedly engaged into the threaded bore 17 1 until the engage collar portion 22 engages with and abuts against the outer wall surface of the cylinder block 11, the inner end of the housing 19 1 does not protrude from the inner end of the threaded bore 17 1 into the cooling water passageway 14. The resilient membrane 18 1 is formed from rubber, synthetic resin or a metal which is reinforced with fabric, synthetic fiber or glass fiber for the purpose of enhancing the durability of the resilient membrane 18 1 . The resilient membrane 18 1 is secured at its peripheral edge to the inner end of the housing 19 1 , for example, by baking or the like to close the inner end of the bottomed cylindrical housing 19 1 . Moreover, the peripheral edge of the resilient membrane 18 1 is secured to the inner end of the housing 19 1 , for example, flush with the inner end of the housing 19 1 , so that it cannot protrude from the inner surface of the outer wall 11b of the cylinder block 11 into the cooling water passageway 14. It is desirable that the positions of disposition of the threaded bore 17 1 and the vibration absorbing means 16 1 are near a location in which the piston 12 gives a blow against inner surfaces of the cylinders 13 2 and 13 3 . It is known that the timing of generation of a slap vibration to a crank angle is within 25 degrees before and after a top dead center position of the piston 12. Therefore, if a sum of the amount of piston displaced at 25 degrees before and after the top dead center and the axial length of the piston 12 is represented by A in Fig. 2, it is desirable that the threaded bore 17 1 and the vibration absorbing means 16 1 are disposed in a range of A from the upper surface of the cylinder block 11. The experiment made by the present inventors showed that the velocity [mm/s] of a vibration produced by a blow applied to each of the cylinders 13 1 , 13 2 , 13 3 and 13 4 by the piston 12 is varied as shown in Fig.4 in the direction of the arrangement of the cylinders 13 1 , 13 2 , 13 3 and 13 4 and is increased at portions corresponding to the sleeve bore centers of the second and third cylinders 13 2 and 13 3 lying at intermediate portions in the direction of the arrangement of the cylinders 13 1 , 13 2 , 13 3 and 13 4 . Therefore, it is desirable that the threaded bore 17 1 and the vibration absorbing means 16 1 are disposed in and on the outer wall 11b of the cylinder block 11 at locations corresponding to the sleeve bore centers of the second and third cylinders 13 2 and 13 3 , as the cylinder block 11 is viewed from a side perpendicular to the direction of the arrangement of the cylinders 13 1 , 13 2 , 13 3 and 13 4 . The operation of the first embodiment will be described below. If the pistons 12 collide against the inner surface of the cylinders 13 1 , 13 2 , 13 3 and 13 4 to vibrate the cylinders 13 1 , 13 2 , 13 3 and 13 4 , because the small gaps exist between the outer surfaces of the pistons 12 and the inner surfaces of the cylinders 13 1 , 13 2 , 13 3 and 13 4 , respectively, such vibration is transmitted to the non-compressible cooling water in the cooling water passageway 14 to induce a variation in pressure of the cooling water. However, the threaded bores 17 1 are provided in the outer wall 11b of the cylinder block 11 at locations facing the water passage portion 14a of the cooling water passageway 14, and the vibration absorbing means 16 1 are mounted on the outer wall 11b to close the threaded bores 17 1 . The vibration absorbing means 16 1 includes the resilient membrane 18 1 having one surface facing the cooling water passageway 14, and the housing 19 1 which defines the space area 20 1 between the housing 19 1 and the other surface of the resilient membrane 18 1 . Therefore, the variation in pressure of the cooling water is absorbed by flexure of the resilient membrane 18 1 and hence, the vibrating force applied from the cooling water to the outer wall 11b of the cylinder block 11 is effectively reduced. Moreover, the space area 20 1 faced by the other surface of the resilient membrane 18 1 is covered with the housing 19 1 and hence, the sound due to the vibration of the resilient membrane 18 1 cannot be radiated from the housing 19 1 to the outside, and the piston slap sound radiated from the cylinder block 11 can be effectively reduced. Further, since the vibration absorbing means 16 1 are mounted to portions of the outer wall surface of the cylinder block 11, an increase in weight of the cylinder block 11 due to the mounting of the vibration absorbing means 16 1 can be suppressed to an extremely small value. A result of the verification concerning the acceleration [m/s 2 ] of the outer wall 11b of the cylinder block 11 at a location corresponding to the third cylinder 13 3 is as shown in Fig.5. As is apparent from Fig.5, in the prior art cylinder block including no vibration absorbing means 16 1 , the acceleration is relatively high as shown by a broken line, and in the internal combustion engine according to the present invention, the acceleration is effectively reduced as shown by a solid line, whereby it can be seen that the piston slap sound can be effectively reduced by the vibration absorbing means 16 1 according to the present invention. In addition, since the peripheral edge of the resilient membrane 18 1 does not protrude from the inner surface of the outer wall lib of the cylinder block 11 into the cooling water passageway 14, the flow of the cooling water in the cooling water passageway 14 by the resilient membrane 18 1 is not obstructed. Thus, the flow of the cooling water in the cooling water passageway 14 is smooth, thereby maintaining the cooling performance at the same level as in the prior art water-cooled type internal combustion engine equipped with no vibration absorbing means 16 1 . Moreover, the housing 19 1 protrudes outwards from the outer wall surface of the cylinder block 11, and the space area 20 1 is defined between the housing 19 1 and the resilient membrane 18 1 . Therefore, even if a variation in temperature of the cooling water is produced, the temperature of the gas in the space area 20 1 is varied only in a small amount, and the variation in pressure in the space area 20 1 can be suppressed to a very small level. Thus, the vibration characteristic of the resilient membrane 18 1 can be stabilized, even during a variety of operations of the engine, and an excellent vibration absorbing effect can be obtained. Further, since the housing 19 1 of the vibration absorbing means 16 1 is detachably mounted to the outer wall surface of the cylinder block 11, and the resilient membrane 18 1 is secured to the housing 19 1 , the replacement and maintenance of the resilient membrane 18 1 can be easily performed. Fig.6 illustrates a second embodiment of the present invention, wherein portions or components corresponding to those in the first embodiment are designated by like reference characters. A through-bore 17 2 is provided in an outer wall 11b of a cylinder block 11, and a vibration absorbing means 16 2 is mounted to the outer wall 11b of the cylinder block 11 to close the through-bore 17 2 . The vibration absorbing means 16 2 includes a collar 26 which is liquid-tightly press-fitted into the through-bore 17 2 , a resilient membrane 18 2 having one surface facing the cooling water passageway 14, and a housing 19 2 which is detachably mounted to the collar 26 to define a space area 20 2 between the housing 19 2 and the other surface of the resilient membrane 18 2 . The collar 26 is cylindrically made from a metal material, and has an inner end which is press-fitted into the through-bore 17 2 so that it does not protrude from the inner surface of the outer wall 11b of the cylinder block 11 into the cooling water passageway 14, and an outer end which protrudes outwards from the outer wall 11b of the cylinder block 11. The resilient membrane 18 2 is integrally provided with a fitting cylindrical portion 27 into which the protrusion of the collar 26 from the cylinder block 11 is fitted. By fitting of the collar 26 into the fitting cylindrical portion 27, the resilient membrane 18 2 closes the outer end of the collar 26 with its one surface facing the water passage portion 14a of the cooling water passageway 14. The housing 19 2 is formed into a bottomed cylindrical shape from a synthetic resin, so that the fitting cylindrical portion 27 having the collar 26 fitted therein can be fitted into the housing 19 2 . A space area 20 2 is defined between the closed outer end of the housing 19 2 and the resilient membrane 18 2 and faced by the other surface of the resilient membrane 18 2 . Further, a slit 28 extending axially along the cylindrical portion of the housing 19 1 is provided at the opened end of the housing 19 2 in order to facilitate fitting over the fitting cylindrical portion 27, and the outer periphery of the opened end of the housing 19 2 having the fitting cylindrical portion 27 fitted therein is clamped by a clamping band 29 in a manner to ensure a sealability between the collar 26 and the fitting cylindrical portion 27. Even according to the second embodiment, an effect similar to that in the first embodiment can be provided and moreover, by the fact that the housing 19 2 is made from a synthetic resin, the weight of the vibration absorbing means 16 2 can be reduced. Fig.7 illustrates a third embodiment of the present invention, wherein portions or components corresponding to those in the previously described embodiments are designated by like reference characters. A through-bore 17 3 is provided in an outer wall 11b of a cylinder block 11, and a vibration absorbing means 16 3 is mounted to the outer wall lib of the cylinder block 11 to close the through-bore 17 3 . The vibration absorbing means 163 includes a collar 30 which is liquid-tightly press-fitted into the through-bore 17 3 , a resilient membrane 18 3 having one surface facing the water passage portion 14a of the cooling water passageway 14, and a housing 19 3 which is detachably mounted to the collar 30 to define a space area 20 3 between the housing 19 3 and the other surface of the resilient membrane 18 3 . The collar 30 is cylindrically made from a metal material, and has an inner end which is press-fitted into the through-bore 17 3 so that it does not protrude from the inner surface of the outer wall 11b of the cylinder block 11 into the water passage portion 14a of the cooling water passageway 14, and an outer end which protrudes outwards from the outer wall 11b of the cylinder block 11. A peripheral edge of the resilient membrane 18 3 is secured to the inner end of the collar 30, for example, by baking, in such a manner that the inner end of the collar 30 is closed by the resilient membrane 18 3 . Moreover, the peripheral edge of the resilient membrane 18 3 is secured to the inner end of the collar 30, for example, flush with the inner end of the collar 30, in such a manner that it does not protrude from the inner surface of the outer wall 11b of the cylinder block 11 into the water passage portion 14a of the cooling water passageway 14. The housing 193 is formed into a bottomed cylindrical shape and integrally provided with a cylindrical portion 31 into which the protrusion of the collar 30 from the cylinder block 11 is liquid-tightly fitted. The space area 20 3 is defined in the collar 30 between the closed outer end of the housing 19 3 and the resilient membrane 183 and faced by the other surface of the resilient membrane 18 3 . According to the third embodiment, the operation for mounting and removing the collar 30 to and from the cylinder block 11 and thus the operation for replacing the resilient membrane 18 3 is more difficult than the first and second embodiments. However, it is possible to effectively reduce the piston slap sound, while avoiding an increase in weight of the cylinder block 11, and to avoid hindering the flow of cooling water in the cooling water passageway 14 to the utmost by the resilient membrane 18 3 to maintain the cooling performance at the same level as in the prior art. Further, it is possible to stabilize the vibration characteristic of the resilient membrane 18 3 to provide an excellent vibration absorbing effect even during a variety of operations of the engine. Figs. 8 and 9 illustrate a fourth embodiment of the present invention. Fig.8 is a side view of a portion of a cylinder block, and Fig.9 is a sectional plan view taken along a line 9-9 in Fig.8. Through-bores 17 4 are provided in an outer wall lib of a cylinder block 11 at portions corresponding to center locations of second and third cylinders 13 2 and 13 3 , respectively. A vibration absorbing means 16 4 is mounted to the outer wall 11b of the cylinder block 11 from the side of an outer surface in a manner to close the through-bores 17 4 . The vibration absorbing means 16 4 includes a pair of resilient membranes 18 4 each having one surface facing the water passage portion 14a of the cooling water passageway 14, a clamp plate 32 which clamps the resilient membranes 18 4 between the clamp plate 32 and the outer surface of the cylinder block 11, and a housing 19 4 fastened to the cylinder block 11 along with the clamp plate 32 to define a single common space area 20 4 between the housing 19 4 and the other surfaces of the resilient membranes 18 4 . The outer surface of the outer wall 11b of the cylinder block 11 is provided with mounting seats 33 faced by outer ends of the through-bores 17 4 , and a recess 34 disposed between the mounting seats 33. The clamp plate 32 is disposed to liquid-tightly clamp the resilient membranes 18 4 , each formed into a disk-like shape, between the clamp plate 32 and the mounting seats 33. The clamp plate 32 is provided with through-holes 35 corresponding to the through-bores 17 4 , and a communication bore 36 disposed between the through-holes 35 and corresponding to the recess 34 in the cylinder block 11. The housing 19 4 is formed to cover the clamp plate 32 from the outside. The outer periphery of the housing 19 4 and the clamp plate 32 are commonly fastened at their plural circumferentially spaced points to the cylinder block 11 by bolts 37. In a state in which the clamp plate 32 and the housing 19 4 clamping the resilient membranes 18 4 between them and the mounting seats 33 have been fastened to the cylinder block 11, end faces of the resilient membranes 18 4 commonly face the space area 20 4 defined between the housing 19 4 and the cylinder block 11 to have a relatively wide volume. According to the fourth embodiment, since the vibration absorbing means 16 4 corresponding to the second and third cylinders 13 2 and 13 3 has the single housing 19 4 common to the resilient membranes 18 4 , it is possible to provide reductions in number of parts and number of assembling steps. Alternatively, the clamp plate 32 and the housing 19 4 may be formed integrally with each other. Fig. 10 illustrates a fifth embodiment of the present invention. An outer wall 11b of a cylinder block 11 is provided with a single or a plurality of (two in this embodiment) transverse ribs 40 and 41 extending in the direction of the arrangement of the cylinders 13 1 , 13 2 , 13 3 and 13 4 (see Fig. 1), and four longitudinal ribs 42, 43, 44 and 45 extending substantially in parallel to axes of the cylinders 13 1 , 13 2 , 13 3 and 13 4 at locations corresponding to the centers of the cylinders 13 1 , 13 2 , 13 3 and 13 4 . Moreover, the positions of disposition of the transverse ribs 40 and 41 are limited into a range A' provided by addition of one half of the width of the ribs 40 and 41 to the range A shown in the first embodiment. Vibration absorbing means 16 1 , for example, as described in the first embodiment, are disposed on the outer wall 11b of the cylinder block 11 at locations corresponding to the second and third cylinders 13 2 and 13 3 , respectively. According to the fifth embodiment, the rigidity of the cylinder block 11 at a portion at which the acceleration produced with the piston slap is especially large can be enhanced by both of the transverse ribs 40 and 41 and the longitudinal ribs 43 and 44 corresponding respectively to the second and third cylinders 13 2 and 13 3 , and the piston slap sound can be further effectively reduced by cooperation of the enhancement in rigidity provided by the other longitudinal ribs 42 and 45 with the vibration absorbing effect provided by the vibration absorbing means 16 1 . Fig. 11 illustrates a sixth embodiment of the present invention. A threaded bore 17 5 as a through-bore is provided in an outer wall 11b of a cylinder block 11. A vibration absorbing means 16 5 is mounted to the outer wall 11b of the cylinder block 11 in a manner to close the threaded bore 17 5 . The vibration absorbing means 16 5 includes a resilient membrane 18 5 which is secured, for example, by baking, to an inner end of a cylindrical support plate 46 liquid-tightly fitted into the threaded bore 17 5 , and which resilient membrane 18 5 has one surface facing the water passage portion 14a of the cooling water passageway 14. The other surface of the resilient membrane 18 5 faces an external open space as a space area. Even when the space area faced by the other surface of the resilient membrane 18 5 is not a closed space as in the sixth embodiment, the piston slap sound can be reduced by absorbing the variation in pressure of the cooling water by the flexure of the resilient membrane 18 5 . Fig. 12 illustrates a seventh embodiment of the present invention. A pump housing 48 of a water pump 47 is coupled to the cylinder block 11 to constitute a portion of the engine body E. The water pump 47 is comprised of a pulley 50 mounted at a protrusion (from the pump housing 48) of a rotary shaft 49 rotatably supported in the pump housing 48 for inputting power from a crankshaft (not shown), and an impeller 51 secured to the rotary shaft 49 within the pump housing 48. An outlet passage 14b is defined between the pump housing 48 and the cylinder block 11 and constitutes a cooling water passageway 14 together with a water passage portion 14a which surrounds the cylinders 13 1 , 13 2 , 13 3 and 13 4 (see Fig.1). Thus, cooling water is discharged from the outlet passage 14b into the water passage portion 14a as shown by an arrow in Fig.12 in response to the rotation of the impeller 51. A threaded bore 17 1 , for example, as a through-bore is provided in that portion of the pump housing 48 serving as an outer wall of the engine body E, which faces the outlet passage 14b of the cooling water passageway 14. A vibration absorbing means 16 1 as described in the first embodiment is mounted to the pump housing 48 in a manner to close the threaded bore 17 1 . When the construction is such that the vibration absorbing means 16 1 is disposed in the vicinity of the water pump 47 for circulating the cooling water as in the seventh embodiment, it is possible to reduce the piston slap sound and to effectively prevent the generation of a cavitation in the water pump 47. Although the embodiments of the present invention have been described in detail, it will be understood that the present invention is not limited to the above-described embodiments, and various modifications in design may be made without departing from the scope of the invention defined in claims. For example, the present invention is not limited to the multi-cylinder water cooled-type internal combustion engines including three or more cylinders, but is also applicable to a single-cylinder or two-cylinder water cooled-type internal combustion engine.

Claims: A water-cooled type internal combustion engine comprising a cylinder (13 1 , 13 2 , 13 3 , 13 4 ) provided in a cylinder block (11) of an engine body (E) and having a piston (12) slidably received in the cylinder, and a cooling water passageway (14) defined in the engine body and including a water passage portion (14a) surrounding the cylinder wherein said internal combustion engine further includes a through-bore (17 1 ;17 2 ;17 3 ;17 4 ;17 5 ) provided at that portion of an outer wall (11b) of the engine body which faces the cooling water passageway, and means (16 1 ;16 2 ;16 3 ;16 4 ;16 5 ) mounted to the outer wall surface of the engine body to close said through-bore, said means including a resilient membrane (18 1 ;18 2 ;18 3 ;18 4 ;18 5 ) positioned adjacent said through-bore and having a first surface facing the cooling water passageway and a second surface facing outwardly of the engine block, and a housing (19 1 ;19 2 ;19 3 ;19 4 ;19 5 ) covering said resilient membrane, characterized in that said means is a vibration absorbing means and said housing forms a space area (20 1 ;20 2 ;20 3 ;20 4 ) between said second surface and said housing, said space area being of a volume for effectively absorbing vibrations transmitted through the cooling water. A water-cooled type internal combustion engine as claimed in claim 1, wherein a plurality of said cylinders (13 1 ,13 2 ,13 3 ,13 4 ) equal to three or more are disposed in parallel in said cylinder block (11), and said vibration absorbing means (16 1 ;16 2 ;16 3 ;16 4 ;16 5 ) is mounted to said cylinder block at an intermediate location in a direction of arrangement of said cylinders (13 1 ,13 2 ,13 3 ,13 4 ). A water-cooled type internal combustion engine as claimed in claim 1 or 2, wherein said through-bore (17 1 ;17 2 ;17 3 ;17 4 ;17 5 ) is located at a position adjacent to said piston (12) in a top dead center position of the piston. A water-cooled type internal combustion engine as claimed in claim 1, 2 or 3, wherein said through-bore (17 1 ) is threaded, said housing is a bottomed cylindrical housing (19 1 ) with external threads (21) on an open end of said housing threadedly engaging said through-bore, and said resilient membrane (18 1 ) is mounted in said open end of said housing. A water-cooled type internal combustion engine as claimed in claim 1, 2 or 3, wherein said vibration absorbing means (16 2 ,16 3 ) includes a collar press-fit (26;30) into said through-hole (17 2 ;17 3 ). A water-cooled type internal combustion engine as claimed in claim 5, wherein said resilient membrane (18 2 ) is mounted on an outer end of said collar (26) and spaced from said outer wall (11b). A water-cooled type internal combustion engine as claimed in claim 6, wherein said resilient membrane (18 2 ) is in the form of a cup with a cylindrical wall (27) surrounding said collar (26) and a bottom having said first surface and said second surface. A water-cooled type internal combustion engine as claimed in claim 7, wherein said housing is a bottomed cylindrical housing (19 2 ) with a cylindrical wall surrounding said cylindrical wall (27) of said resilient member (18 2 ). A water-cooled type internal combustion engine as claimed in claim 8, further including a cylindrical clamp (29) clamping said housing (19 2 ) cylindrical wall to said resilient member (18 2 ) cylindrical wall (27). A water-cooled type internal combustion engine as claimed in claim 8 or 9, wherein a bottom wall of said bottomed cylindrical housing (19 2 ) is spaced from said second surface of said resilient membrane (18 2 ) for forming said space area (20 2 ) therebetween. A water-cooled type internal combustion engine as claimed in claim 5, wherein said resilient membrane (18 3 ) is mounted on an inner end of said collar (30). A water-cooled type internal combustion engine as claimed in claim 11, wherein said housing is a bottomed cylindrical housing (19 3 ) with a cylindrical wall (31) mounted on an exterior cylindrical wall of said collar (30). A water-cooled type internal combustion engine as claimed in any of claims 1 to 3, wherein two said through-bores (17 4 ) are provided with one said through-bore located opposite a second said cylinder (12) adjacent to said one said cylinder, a said resilient membrane (18 4 ) positioned to cover each said through-bore, and said housing (19 4 ) extending over and covering, in spaced relationship, both said resilient membranes and both said through-bores. A water-cooled type internal combustion engine as claimed in claim 1 or 2, or any of claims 4 to 12 when not dependent on claim 3, wherein said through-bore (17 1 ;17 2 ;17 3 ;17 4 ;17 5 ) is located in a water pump housing (48) of the engine body (E), said through-bore located downstream from a water pump (47).

Inventors: KAWAI NORIAKI, NOZAWA YASUJI, SAKASHITA MASAO, TAKEDA NAOAKI, KAWAI, NORIAKI, NOZAWA, YASUJI, SAKASHITA, MASAO, TAKEDA, NAOAKI
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1997
Main classification: F02F1
IPC codes: F02B75, F02F7, F02F1