WO1991015690A1

WO1991015690A1 - Metallic gasket

Info

Publication number: WO1991015690A1
Application number: PCT/JP1991/000452
Authority: WO
Inventors: Nobuo Yoshino
Original assignee: Kabushiki Kaisha Ket And Ket
Priority date: 1990-04-04
Filing date: 1991-04-04
Publication date: 1991-10-17
Also published as: KR100190597B1

Abstract

A metallic gasket according to the present invention is constructed such that increased thickness portions (Ti) surrounding combustion chamber holes (6), respectively, are formed on a base plate (1), a bead (1a) formed on the base plate strides over a stepped portion formed by the increased thickness portion, and a load of the bead is gradually increased from a bolted portion toward a combustion chamber hole, so that sealing performance of the bead can be effectively displayed in accordance with a gap between mating surfaces produced at the time of bolting a cylinder head in a multi-cylinder engine. Further, the raised shapes of the bead around the combustion chamber hole in the vicinity of the bolted portion are formed asymmetrical with each other on the side of the increased thickness portion and on the side of a non-increased thickness portion (Td), namely, the shape of the bead on the side of the non-increased thickness portion is formed into a small curve to increase a spring constant, and the shape of the bead on the side of the increased thickness portion is formed into a large curve or a straight slope to make a spring constant thereof smaller than that on the side of the non-increased thickness portion, whereby the load of the bead on the side of the increased thickness portion at the time of the bolting is decreased, so that the degree of localized adherence of the increased thickness portion around the combustion chamber hole in the vicinity of the bolted portion can be improved.

Description

Satsuki Itoda β Metal Gasket Technical Field

The present invention relates to a metal gasket having a bead surrounding a combustion chamber hole for sealing a mating surface between a cylinder head and a cylinder port of an internal combustion engine, and particularly to a cylinder head in a multi-cylinder engine. The present invention relates to a metal gasket that eliminates troubles generated from a joint surface between fuel holes when bolts are fastened to bolts. BACKGROUND ART In order to fasten a cylinder head and a cylinder opening of an internal combustion engine, a metal gasket having a bead surrounding a fuel hole is interposed at a joint surface of the two, and is fixed at a predetermined position. By bolt fastening, the bead is elastically deformed by the bolt tightening force when fastening the cylinder head, and an elastic seal line is formed on the mating surface by the elastic restoring force and elastic restoring amount at the time of this elastic deformation. Thus, the mating surface is sealed and the distortion of the mating surface is followed to maintain the sealing effect.

However, since the bolt tightening force decreases as the bolt is separated from the bolt fastening portion, the gap between the mating surfaces at the portion more distant from the bolt fastening portion than near the bolt fastening portion increases, and the sealing surface by the bead becomes larger. The pressure will drop.

Especially in the case of a multi-cylinder engine, the mating surface from the bolt fastening part to the circumference of the fuel hole between the bolt fastening part shafts, the mating surface between the bolt fastening part shafts, and the fuel; The gap between the gasket and the gasket surface gradually increases, causing a significant blow-through force, especially between the fuel holes, and the gasket surface is hit by the explosion pressure. The bead around the part also tended to generate a settling force, which reduced the seal surface pressure, which caused further blow-through and loosening of the tightening bolt, which resulted in ^^.

Hereinafter, the change in the gap amount at each part of the mating surface will be described with reference to FIG.

Fig. 11 (a) is a sectional view taken along the line AA in Fig. 11 (d) showing a conventional metal gasket, and a characteristic diagram showing the relationship between the amount of deflection of the metal gasket, the bead height, and the load. Fig. 11 (b) is a cross-sectional view taken along line B-B of Fig. 11 (d) and its characteristic diagram. Fig. 11 (c) is a cross-sectional view taken along line C-C of Fig. 11 (d). Fig. 11 (d) is a schematic plan view of a cylinder head of a multi-cylinder engine, and Fig. 11 (e) is equivalent to the A-A section in Fig. 11 (a). FIG. 4 is a partial cross-sectional view in which a metal gasket is interposed between engine mating surfaces.

In Figs. 11 (a) to (c), H51 to H53 are the initial height of the bead, h511 to h531 are the beads ¾ * after tightening, and h512 to h532 are the beads after the engine durability test. Remaining bead, C511-C531 is the amount of bead set after bolt fastening, C512-C532 is the amount of bead set after endurance test, 551-53 is the amount of bead deflection, P51-P53 is Bead load after engine endurance test, S5 is the strike of the j ^ iUil enclosure end, soda amount, g51, g52, and g53 are in order after A-A, B-B, C-C cross-section bolt tightening The gap around the periphery of the combustion chamber hole after the engine durability test is shown.

As shown in FIGS. 11 (a) to 11 (c), this conventional metal gasket is composed of a sub-plate 52 formed of a bead 51a formed on a substrate 51 and a fuel hole extending from the concave side to the convex side. The thickness-increased portion 50 is formed by forming a folded portion 52 a by folding back to the 42-side hem portion.

As shown in Fig. 11 (e), when this metal gasket is interposed on the engine mating surface and tightened with bolts 41, the gap between the mating surfaces around the fuel holes 42 at each location is Due to the difference between the bolt fastening force and the stiffness of the engine components, the distance increases from the bolt fastening part 41 to g51 <g52 <g53.

In this case, in the A-A cross section having the minimum gap such that g51 becomes zero, the effective bending amount of the bead 51a is reduced by the folded portion 52a being overlapped on the projecting side of the bead 51a. As a result, the thickness of the gasket surface due to the explosive force of the bead 51 a decreases due to the effect of the thickened portion 50, but in the C-C section having the maximum gap g53, the sealing function is provided. However, the thickened portion 50 floats between the mating surfaces: on the other hand, the bead of the bead 5 1a is increased by increasing the load, and the force of the explosion pressure increases as the load increases. As a result, the sealing function of the bead 51 a due to settling decreases.

To cope with this, in order to fill the gap g53 around the combustion chamber hole 42 with a thickness corresponding to the gap g53 so as to fill the gap g53, even if the gap g53 is of the same model, Separately, since it changes depending on the tightening order, it has the opposite effect depending on the thickness change setting, and it is also difficult to change the thickness itself.

SUMMARY OF THE INVENTION The present invention has been made in view of such problems of the conventional technology, and has a bead sealing function in a multi-cylinder engine according to a gap between mating surfaces generated when bolts are fastened to a cylinder. to ensure a uniform sheet one Honoré I ¹ production capability of the entire engine mating surface by effectively exhibit the metal gasket, Seo Bok of combustion ^^ L 1 enclosed gap explosion pressure by tightening of various vibrations such as A metal gasket that protects from the conditions and eliminates the settling of the bead, improves the durability of the bead, secures the sealing surface pressure, prevents blow-through, and does not loosen the tightening bolt. The purpose is to do. Disclosure of the invention

According to the present invention, a metal gasket substrate used in a multi-cylinder engine is provided with a thickness increasing portion surrounding each of the holes, and a bead formed around the fuel on the substrate is provided with a front lightning richness increasing portion. The bead load is formed so as to gradually increase along the periphery of the fuel hole from the bolt fastening part, and then to the cylinder, near the bolt fastening part for the sod fastening. The dog is formed symmetrically or asymmetrically on the side of the Hi-height-increased part and the thickness of the so-large part. Beads By setting the constant to be large, the bead dog with the thickness 增 large part is formed into a large curved shape or a fi fountain slope and the panel constant is made smaller than the thickness 側 large part side, so that bolt fastening The sealing surface pressure between the combustion chamber holes at the time is increased to ensure the sealing performance of the entire engine mating surface. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a view showing an embodiment of the present invention. FIG. 1 (a) is a cross-sectional view taken along the line A--A of FIG. 1 (d), and its characteristic diagram, and FIG. Fig. 1 (d) is a cross-sectional view taken along line B-B and its characteristics. Fig. 1 (c) is a cross-sectional view taken along line C-C of Fig. 1 (d) and its characteristics. Fig. 1 (d) is air-conditioned. Fig. 1 (e) is a partial cross-sectional view of a cylinder head of a cylinder engine with a metal gasket interposed between the engine mating surfaces corresponding to the A-A cross section in Fig. 1 (a). You.

FIG. 2 is a view showing various (first to fifth) modifications of the metal gasket having the symmetrical bead shown in FIG. 1, in which A-A section, B-B section, C 1C section corresponds to FIGS. 1 (a) to 1 (c) in order.

FIGS. 3 to 5 are diagrams showing specific examples of metal gaskets and soots having the symmetrical beads shown in FIG. 1, and FIG. 3 (a) shows the first type C-C of FIG. Fig. 3 (b) is a schematic diagram showing the bead seal line of the metal gasket in Fig. 3 (a), when the section between the combustion chamber holes in the cross section is "narrow". 4 (a) and (b) are cross-sectional views taken along the line A--A, BB, C--C of the fourth type of FIG. 2, and FIG. 5 (a) is a first type of the first type of FIG. Partially cut-away perspective view of the metal gasket in the case of “expansion between fuel holes in C section”, and FIG. 5 (b) is a schematic diagram showing a bead seal line of the metal gasket of FIG. 5 (a). FIG.

6 (a) to 6 (e) are views showing another embodiment of the present invention. FIG. 6 (a) is a sectional view taken along line A--A in FIG. Fig. 6 (b) is a sectional view taken along the line BB of Fig. 6 (d) and its characteristic diagram. Fig. 6 (c) is a sectional view taken along the line C-C of Fig. 6 (d) and its characteristic diagram. Fig. 6 (d) is a schematic plan view of the cylinder head of a multi-cylinder engine, and Fig. 6 (e) is a metal gasket interposed between engine mating surfaces corresponding to the A-A section in Fig. 6 (a). FIG.

FIG. 7 is a view showing various modifications (types 1 to 16) of the metal gasket having the asymmetrical beads shown in FIG.

FIGS. 8 to 10 are diagrams showing a specific configuration example of a metal gasket having an asymmetrical bead shown in FIG. 6, and FIG. (I) A partially cutaway perspective view of the metal gasket when the C section is “sandwich”, FIG. 8 (b) is a schematic view showing the bead seal line of the metal gasket of FIG. 8 (a), and FIG. 9 ( a) is a sectional view taken along the line A-A in FIG. 8 (a), FIG. 9 (b) is a sectional view taken along the line B—B in FIG. 8 (a), and FIG. 9 (c) is a sectional view in FIG. ) Of Fig. 10 (a) is a partially cutaway perspective view of the metal gasket when the C-C cross section of the fourth type of Fig. 7 is "Expanded J," Fig. 10 ( b) is a partial cut between the fuel gas holes 6 and 6 in the case of the “C-C FIG. 10 (c) is a schematic view showing a bead seal line of the metal gasket of FIG. 10 (a), and FIG. 11 is an explanatory view of a conventional metal gasket. Fig. 11 (a) is a cross-sectional view taken along line A-A in Fig. 11 (d) and its characteristic diagram. Fig. 11 (b) is a cross-sectional view taken along line B-B and its characteristic diagram in Fig. 11 (d). ) Is a cross-sectional view of the same line C-C and its characteristics.Fig. 11 (d) is a schematic plan view of a cylinder for a multi-cylinder engine, and Fig. 11 (e) is Fig. 11 (a). ) Is a partial cross-sectional view in which a metal gasket is interposed between engine mating surfaces corresponding to an A-A cross section. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, the present invention will be described in more detail with reference to the drawings.

1st crane example 1

In Fig. 1 (a) to (c), H11 to H13 are the initial height of the bead, hill to hl31 are the remaining beads after bolting, hll2 to hl32 are the remaining beads after the engine endurance test, and Clll to C131 is the amount of bead set after bolt fastening, C112 to C132 is the amount of bead set after engine durability test, δ11 to δ13 is the bead deflection, Ρ11 to Ρ13 is the engine endurance test Later bead load, S 1 is the edge of the ^ 11 U11 surrounding edge, 'gl, gl gl2, gl3 are the engine endurance test after bolt fastening on A-A, B-B, C-C sections The gap around the peripheral edge of the combustion chamber hole is shown below.

The metal gasket and the source shown in FIGS. 1 (a) to 1 (c) correspond to the beads 1a formed on the substrate 1 made of an elastic metal plate surrounding the fuel holes 6 and from the soft metal plate. The wedge stopper 2a is formed by folding the sub-plate 2 formed from the convex side to the middle of the concave side of the bead 1a to form a thickened portion Ti, and the bead 1a is increased in thickness to the thickened portion Ti. Projection height of bead 1a because it straddles section Td; ^ Wedge dropper 2a does not extrude, and the sealing function at each part of the mating surface depends only on the load of bead 1a That is.

Therefore, the width of the bead 1a is reduced to W11> W12> W13 as the bolts become closer to the periphery of the hole 6 between the bolted joints 11 and 1 from the vicinity of the bolted joint 11 and the width of the bead 1a is reduced. By increasing the protruding height to H11 <H12 <H13, the bead load between the mating surfaces of each part is made uniform, and the thickness 增 large part Ti, Ti straddles between the fuel holes 6 and 6. By adapting the width W13 and Og H13 to the gap due to engine distortion, it is possible to exert uniform bead surface pressure regardless of the position between the mating surfaces. Examples of the metal gasket to which the present invention is applied include the first to fifth types shown in FIG.

In each of the first to fifth types of metal gaskets, the bead 1a provided around both the combustion holes of the substrate 1 according to the present invention straddled the thickened portion Ti and the thickened large portion Td. In the first type, the auxiliary substrate 2 ′ is folded from the convex side to the middle of the concave side of the bead 1 a to form a wedge stopper 2 ′ a to form a thickened portion Ti, The seed is formed by folding the edge of the auxiliary substrate 2 "on the concave side of the bead 1a Forming the wedge stopper 2 "a to form a thickened portion Ti, and the third type increases the thickness by attaching the auxiliary plate 8 from the edge of the medullary hole to the middle of the concave side of the bead 1a. In the fourth type, the intermediate plate 3 is provided with a step 3a, and the auxiliary board 2 is formed along the step 3a at the edge of the combustion chamber hole to form a thickened portion Ti by a edge stopper 2a. In addition, a substrate 1 having beads 1 a on both sides thereof is provided, and the fifth type is configured in the same manner as the fourth type except that the fourth type intermediate plate 3 is not provided with a step 3 a, and the other types are not provided. .

The intermediate plate 3 used in the fourth type is provided with a step 3a in order to make the thickness increase on both sides of the gasket substantially the same. This structure is already known in Japanese Patent Application Laid-Open No. Sho 644-65367, but the structure described in this document is also interposed between the combustion chamber holes due to the positional relationship between the bead and the large part. There is a step on the plate, and it is difficult to make a step on the narrow part. In contrast, in the case of the present invention, since the thickened portion is formed so as to straddle the bead 1 a force s ′, a space force for providing a step is secured, and a step between the fuel holes is not required. Good, power of application s wide.

Of these metal gaskets of the first to fifth types, Fig. 3 (a) shows the case where the C-C cross section of the first type metal gasket is "narrow", and Fig. 3 ( Fig. 4 (a) and (b) show cross sections A-8, B-B, and C-C of the fourth type metal gasket, respectively, and Fig. 4 (a)-(b) show the C-C cross section of the first type metal gasket. Fig. 5 (a) shows the case where the cross section is "expanded", and Fig. 5 (b) shows the bead line.

The metal gasket shown in Fig. 3 (a) is formed corresponding to the fuel holes 6, bolt holes 11, cooling water holes 12, and oil holes 13 drilled in the cylinder head of a multi-cylinder engine. It is.

Fig. 4 (a) (A-A cross section) is a cross section passing through the combustion chamber hole 6, the cooling water hole 12, the bolt hole 11 and the hole hole 13, and the substrate 1 has the combustion holes 6, 6 The fuel beads surrounding the fuel tank 1a, the cooling water seals 1 2 surrounding the cooling water seal beads 1b, the oil seals 13 surrounding the oil seal beads 1c (Id), the outer periphery of the gasket A bead 1 e for oil atmosphere is formed along with the sub-plate 2 on the convex side of the bead 1 a of the substrate 1, and it bends around the fuel hole 6 to the middle of the recess of the bead 1 a. By forming the edge stopper 2a (thickness increasing part Ti), the bead 1a straddles the edge strike, the soaper 2a and the other part (non-thickness increasing part Td). There is.

As shown in Fig. 4 (a), the seal bead 1a for the listening chamber is similar to Fig. 1 (a) around the combustion chamber hole 6 (A-A cross section) near the bolted portion 11. In addition, between the bolt holes 11 (B-B cross section), as in FIG. 1 (b), and between the holes 6, 6 (C-C cross section), as in FIG. 1 (c). It is. Therefore, as shown in Fig. 3 (b), the inner seal line 1f of the fuel seal bead 1a passes over the wedge cut and the sopa 2a (thickness 增 large part Ti), and the combustion chamber The outer seal line 1 J surrounds the hole 6 alone, and the general part other than the wedge stopper 2 a (the part with no increased thickness) Td) constitutes a seal line surrounding each fuel M hole 6. As a result, in the gap (C-C cross section) between each of the holes 6 and 6 which is large enough to bend the gasket when the engine gasket is tightened, the bead 1a is connected to the dispersers 2a and 2a (thickened portions Ti and Ti). ) A force s to straddle the bead load by straddling the competitors, and a force ⁵ ′ to improve the seal surface pressure of the relevant portion. In addition, in each of the fuel M holes 6 (B-B cross section) between the bolt holes 1 1 and 1 1, the bead 1 a of the anti-boat dog is a wedge, the soji stopper 2 a and other general parts (increased thickness). By straddling the part Ti and the thick part Td), it is possible to obtain a bead load suitable for the gasket tightening clearance of that part.

In FIG. 3 (a), the space between the fuel holes 6, 6 is “narrow J”. For example, a single bead 1a is formed, which branches off from the bead and closes to the bolt fastening portion 11 The bead dog whose width gradually increases around the fuel hole 6 changes its appearance, and the seal surface pressure between the bolt fastening portion 1 and the shaft is adjusted according to the amount of clearance between the mating surfaces at each part. In the case of “expansion between the fuel holes 6 and 6”, as shown in Fig. 5 (a), the thickness between adjacent thickened portions Ti and the thickness between the thickened portions Ti increased iJBJ to Td. With the intermediate sub-plate 7 of approximately the same thickness as the part Ti interposed, the inner line 1f 'of the substrate bead 1a is arranged on the surface of the intermediate sub-plate 7 for each thickened part. By straddling the boundary of the intermediate sub-plate 7 with a bead la ′ and arranging the outer line 1 j ′ of the substrate bead 1 a outside the surface of the intermediate sub-plate 7, the deflection of the bead 1 a is reduced as in the above example. Secure, clearance amount It is possible to reduce the load §-up against.

1st 2nd Wei example

FIGS. 6 (a) to 6 (c) are cross-sectional views showing a basic configuration of a metal gasket showing another example of the SS of the present invention, and FIG. 6 (d) shows an outline of the mating surface of the multi-cylinder engine shown in FIG. 6 (d), respectively. Fig. 6 (e) shows a cross-sectional view along line A-A, B-B, C-C in the plan view, and a special order diagram showing the relationship between bead load, bead height and bead deflection, and Fig. 6 (e) shows the metal of the present invention. FIG. 6 (a) is a partial cross-sectional view of the engine with a gasket interposed, taken along line AA of FIG. 6 (a).

In Fig. 6 (a) to (c), H21 to H23 are the initial height of the beads, h211 to h231 are the remaining beads after fastening the bolt, and h212 to h213 are the remaining beads after the durability test. , C211 to C231 are the bead set after bolt fastening, C212 to C232 are the bead set after endurance test, P21 to P23 are the bead load after endurance test, δ21 to δ23 are end of endurance Bead deflection at the time, g22, g23 are gasket surface gaps at the end of endurance, W21 to W23 are bead width, <i »D is ^ hole diameter, and the same sign as in the first example Is used.

The ϋ gasket of the second embodiment is arranged around the ¾ hole 6 near the bolt fastening portion 11 (A-A section) so as to surround the ^ hole 6 of the multi-cylinder engine on the substrate 1 made of an elastic metal plate. Forms an asymmetrical beat 1a "and bolts 1 1

(BB cross section) Between Mjmm ie. 6 (c-c cross section), a ^ W-shaped bead 1a is formed.

Bolt fastening part 1 1 Near! ^ Around hole 6, non- 鄉 bead 1a " A wedge stopper 2a is formed by stacking a sub-plate 2 made of a soft metal plate on the convex side and folding the sub-plate 2 around the fuel hole 6 from the convex side to the concave side of the asymmetric bead 1a ". The asymmetrical bead 1a "is formed so as to straddle the asymmetrical bead 1a" force S thickness increasing part Ti and the other non-large portion Td, and the asymmetrical bead 1a " The bead shape is formed into a small curved shape 1a_2 on the bolted part 11 side (non-increased thickness Td) with the asymmetrical line 21 deviated to the side of the connected part 1 1 offset to increase the panel constant. The bead dog is formed on the combustion hole 6 side (thickness increasing part Ti) in a large curved shape or linearly inclined shape (hereinafter, simply referred to as “large curved shape”) 1a-1 and the panel constant is It is formed to be smaller than the non-increased thickness part Td side.

With such a configuration, around the fuel hole 6 near the bolt fastening part 11, a bolt generated due to the asymmetric bead la ”straddling the wedge stopper 2 a (thickness 增 large part Ti) Increased thickness at the time of fastening Reduce the bead load on the Ti side to improve the partial adhesion of the increased thickness Ti, and adapt the gasket in response to changes in the engine mating surface gap during initial tightening. The wedge effect of the thickened portion Ti can be further exhibited.

In addition, between the bolted portions 11 and 11 (B-B cross section), the symmetrical bead 1a is composed of the edge stopper 2a (thickness, large portion Ti) and the other general portions (thickness 3 It is configured to straddle Sou Obu Td), and between holes 6 and 6 (c-c section), the symmetrical bead 1a straddles the wedge stops 2a and 2a on both sides. Therefore, the seal lines of these beads pass over the edge stopper 2a (thickness increasing portion Ti) on the inner line 1f to individually surround each combustion chamber hole 6, and the outer line 1j Each fuel hole is formed so as to continuously surround each fuel hole 6 through the ^ IS part (thickness Td) other than the stopper 2a, and the fuel gasket of the engine maximizes the bending deflection: ^ hole 6 In the gap between c and c (c-c cross section), the bead load can be increased by straddling the bead 1a force and the S-edge dippers 2a and 2a. Can be improved.

Further, the asymmetric bead 1a "around the combustion chamber hole 6 in the vicinity of the bolt fastening portion 11 is continuously transformed into the symmetric bead 1a between the combustion chamber holes 6, so that the engine is improved. A sealing surface pressure corresponding to the amount of the tightening gap at each part of the mating surface can be exhibited.

As the metal gasket to which the present invention is applied, specific examples such as the first to sixteenth types shown in FIG. 7 are considered.

In FIG. 7, cross sections A—A, B—B, and C—C correspond to the cross sections in FIGS. 6 (a) to (c). In the case of "narrow", there is one symmetrical bead 1a, and in the case of "expansion", two symmetrical beads la and 1a are provided. In the description, ίϋ¾ ± and beads are denoted by reference numeral 1a for both symmetric and asymmetric types, and the reference numerals for the respective components are omitted for the common portions.

In the first type, a flat plate-shaped sub-plate 2 is connected to the) 1 ^ hole 6 side of the substrate 1 by overlapping or overlapping in the form of a ring. Plate 7 interposed In the case of the continuous connection, the flat sub-plate 2 is straddled by the bead 1a as a partial connection in order to enable the bead side.

The second type is the same as the first type, except that the secondary plate 2 is projected on the concave side of the bead 1a in the C-C section, or the secondary plate 2 is along the concave dog of the bead 1a. Are superposed and joined together.

The third type is obtained by bending the end of the substrate 1 toward the burning hole 6 side and superimposing it (overlapping portion 2b). The sub-plate 2 is laminated and the sub-plate 2 is straddled by the bead 1a. In the C-C section, another intermediate flat sub-plate 7 is interposed in accordance with the height of the overlapping portion 2b.

The fourth type is such that the sub-plate 2 is bent from the convex side of the bead 1a to the concave side of the bead 1a toward the listening hole 6 side of the substrate 1, and the sub-plate 2 is straddled by the bead 1a.

The fifth type has a surface plate 9 superimposed on and joined to the sub-plate 2 superposed on the fuel pan hole 6 side, laminated on the substrate 1, and straddling the superposed portion with a bead 1a.

The sixth type is obtained by laminating the substrates 1 and 1 so as to straddle the sub-plate 2 on the side of the burning hole 6 from both sides with each bead 1 a force s.

The seventh type is obtained by further stacking the sub-plate 2 on the convex side of the third type bead 1a. The eighth type is obtained by stacking a surface plate 9 on the concave side of the fourth type bead 1a.

The ninth type is obtained by further stacking another substrate 1 on the side of the third type sub-plate 2 with a bead 1a.

Type 10 is provided with a central intermediate plate 3, a step 3 a is formed on the fuel keyhole 6 side of the intermediate plate 3 except for the C-C cross section, and the sub plate 2 is overlapped with the concave portion as a fiber concave portion and joined. Then, the substrate 1 and the substrate 2 are superimposed so that the bead 1 a has a directional force ^ from both sides, and the bead 1 a is combined with the S step 3 a.

In the first type, the intermediate plate 3 (without the step 3a) is provided at the center, the sub-plate 2 is overlapped on the fuel hole 6 side of the intermediate plate 3, and the bead is provided on the side where the sub-plate 2 is provided. 1a Substrate 1 is stacked so as to straddle the sub-plate 2, and the base 1 is stacked so that the bead convex side of the intermediate plate 3 faces the opposite side.

The 12th type is obtained by stacking the 10th type sub-plate 2 on the convex side of the step 3a and bending it at the fuel hole 6 side to form the overlapped portion 2a in the concave portion of the step 3a.

Type 13 is obtained by stacking sub-plates 2 of type 1 so as to extend to the opposite side of the intermediate plate 3.

In the case of the first four types, the sub-plate 2 of the first two types is made thicker than that of the first two types, and another flat sub-plate 2 is intermittently stacked on the overlapping portion 2a side of the step 3a, and the plate thickness is increased. The thickness was increased by the difference.

The 15th type is obtained by stacking another flat auxiliary plate 8 on the 13th type 2a side. In the 16th type, the intermediate plate 3 is arranged, the sub plate 2 is bent up and down at the fuel hole 6 side, and another sub plate 8 is stacked on the intermediate plate 3 to increase the thickness by the difference: ^ S Things.

Note that the first, third, fourth, seventh to ninth, and first to second-

For 1β species, another intermediate flat subplate 7 is provided between the two beads to ensure the surface pressure between the burners. Further, the intermediate plate 3 used for the type 10 and the type 12 is provided with a step 3a in order to make the thickness increase on both sides of the gasket substantially the same. This configuration is based on the force already known in Japanese Patent Application Laid-Open No. Sho 644-65367. The force described in this document is also due to the positional relationship between the bead and the large part, and the intermediate plate is also provided between the burner holes. There is a drawback in that it is excellent to use a step in the narrow part and to make a step in the narrow part. On the other hand, in the case of the present invention, since the thickness increasing portion Ti is straddled by the bead la force s, no step is required between the combustion chamber holes 6 and 6 and a continuous concave portion is formed. The engine can also be used for Class 1 and Class 13 metal gas kettles.

Among these specific examples, Fig. 8 (a) shows the metal gasket when the C-C cross section of type 4 is "narrow", and Fig. 8 (b) shows its bead line. 8 (a) to 9 (c) show the A--A, B--B, and C-C cross sections of FIG. 8 (a), and show the metal gasket when the fifth type of C--C cross section is "expanded". FIG. 10 (a) shows a second type of metal gasket in FIG. 10 (b), and a common bead line is shown in FIG. 10 (c).

In FIGS. 8 (a) and 10 (a), A--A, B--B, and C--C sections correspond to the respective sections in FIG. 7, and FIGS. 6 (a) through (c) ).

The metal gasket shown in Fig. 8 (a) has fuel holes 6 and bolt holes 11 and? It is formed in correspondence with the reed water hole 12 and the oil hole 13 and the cross-sections A--A, B--B, and C--C in the same figure are as shown in FIGS. 9 (a)-(c). You. Fig. 8 (a) (A-A cross section) is a cross-section passing through the burning hole 6, the cooling water hole 12, the bolt hole (in the above, it is a bolt fastening part) 11, and the oil hole 13. 1 includes a combustion chamber seal bead 1 a surrounding the combustion chamber hole 6 (including the above asymmetrical bead 1 a ″), a cooling water seal bead lb surrounding the cooling water hole 12, and an oil hole 13. The surrounding oil seal bead 1 c and the oil atmosphere bead 1 d provided along the outer periphery of the gasket are formed. Further, the sub-plate 2 is attached to the bead 1 a convex side of the substrate 1, and the fuel The bead 1a is bent halfway into the recess of the bead 1a around the furnace chamber hole 6 to form the wedge stopper 2a, so that the bead 1a becomes the wedge stopper 2a (thickened portion Ti) and other general parts. The part (the non-increased part Td) is straddled.

As shown in FIG. 8 (a), the seal bead 1a for the combustion chamber is similar to that of FIG. 6 (a) in the vicinity of the fuel keyhole 6 (A-A cross section) near the bolt fastening part 11. Similarly, as shown in FIG. 6 (b), between the bolt holes 11 and 11 (B-B section), the fuel; and between the holes 6 and 6 (C-C section) as shown in FIG. 6 (c). It is formed similarly. Therefore, as shown in FIG. 8 (b), the inner seal line 1f of the fuel sealing bead 1a passes over the wedge storage 2a (thickness increasing portion Ti), and each fuel; 6 alone, and the outer seal line 1 j forms a seal line that continuously surrounds each fuel hole 6 through the “^” section (thick Sodabe Td) other than the wedge stopper 2 a. As a result, in the gap between the fuel holes 6 and 6 (C-C cross section), which causes the deflection of the gasket when the engine gasket is tightened, the bead 1a is connected to the edge stoppers 2a and 2a. Straddling As a result, the bead load can be increased, and the sealing surface pressure at the relevant portion can be improved. In addition, in each of the fuel holes 6 (B-B cross section) between the bolt holes 11 and 11, the bead 1 a of the symmetric 开 ^ I dog straddles the edge stop 2 a and the other “^”. This makes it possible to obtain a bead load suitable for the gasket tightening clearance of the portion.

In FIG. 8 (a), a single symmetrical bead 1a is formed between the combustion chamber holes 6 and 6 as shown in the second and fourth types of C-C cross sections (in the case of "narrow"), Branching from the bead, the shape of the asymmetrical bead around the combustion chamber hole 6 near the bolted portion 11 (A-A section) is continuously changed to the dog, and the shape of each bead is changed. The seal surface pressure between the bolt fastening part 1 and the one shaft is adjusted according to the clearance between the mating surfaces.

When the area between the combustion holes 6 is “expanded J”, the surface pressure between the fuels is increased through the intermediate flat sub-plate 7 as shown in FIGS. 10 (a) and 10 (b). Power to secure S

Also, in the case of a structure in which the bead 1a force is branched as shown in the BB section of FIG. 10 (a), another sub-plate 7 is interposed as shown in the C-C section. It is also possible to ensure surface pressure.

In the metal gasket of the first embodiment, an edge stopper 2a is formed on the concave side of the bead 1a, so that the bead 1a has a large thickness Ti and a large portion Td. When the bolt is tightened, the bead 1a thickness 增 the large Ti side force s thickness s thick large part T Bends first under a load greater than that of the d side. Although the degree of adhesion between the mating surfaces on the first side may decrease and the degree of adhesion on the thickness-increased portion Ti may decrease, a gap force ^s may be generated. In the second embodiment, the bolt fastening portion 1 1 Around the combustion chamber hole 6 in the vicinity, the asymmetrical bead 1a "reduces the bead load on the side of the thickened portion Ti when the bolt is fastened due to straddling the wedge stopper 2a (thickened portion Ti). This increases the degree of partial adhesion of the thickened part Ti and reduces the gap between the engine mating surfaces during initial tightening. Rub the gasket Bok and, it is possible to further exhibit the wedge effect of the thickness increasing portion Ti.

In addition, spot welding, seam welding, laser welding, welding, bonding, and the like can be applied to the method of joining the components of the gasket of the present invention, in addition to the bending and crimping method, and the surface of the gasket itself is mainly used for other layers. By applying NBR, fluorine rubber, etc., including the above, it is possible to absorb the processing marks and scratches on the mating surface of the engine, and to increase the ability to inject interlayer seals. Industrial applicability

As described in JiUL, in the metal gasket of the present invention, the substrate is provided with a thickness increasing portion surrounding each of the combustion holes, and the beads formed on the substrate are arranged across the step formed by the thickness increasing portion. Since the load of the bead is formed so as to gradually increase from the bolted portion along the periphery of the hole, the bead is formed in accordance with the gap between the mating surfaces generated when the cylinder head is bolted in a multi-cylinder engine. The seal function can be effectively exerted, and a uniform seal efficiency over the entire engine mating surface is achieved. And secures the gap by tightening the metal gasket around the fuel hole from explosion pressure, vibration, and other conditions, thereby eliminating bead settling and maintaining bead durability and sealing surface pressure. It can be used as a metal gasket, which can prevent blow-through by preventing loosening force S 'from being generated in the tightening bolt.

In addition, the protrusion of the bead around the combustion chamber hole near the bolt fastening part! The dog is formed asymmetrically between the thickened portion and the non-increased portion, and the non-large bead 开 ^ I dog is formed in a small curved shape to increase the panel constant and the thickness. The bead shape on the enlarged part side is formed in a dog-like curved shape or a linearly inclined shape to make it smaller than the panel constant force thickness non-increased part side, so that the thickness at the time of bolt fastening is large. This reduces the bead load on the part, thereby improving the degree of partial adhesion of the thickened part around the fuel hole near the bolt fastening part.

The asymmetric bead dog around the medullar hole near the bolt fastening part and the symmetrical Jl¾ dog bead between the bolt fastening part axis and the fuel keyhole can be continuously changed in shape. By increasing the bead strength between the shafts and between the combustion chamber holes in response to the amount of gap that changes with bolt fastening, it is possible to ensure the seal surface pressure around the fuel MM holes. The thickness of the fuel near the bolt joint: the thickness of the surrounding area. It can compensate well and prevent expansion and contraction of the gap between the engine mating surfaces around the combustion chamber due to the fuel condensing pressure. Also, a stable seal can be achieved by uniformly applying the seal surface pressure to the mating surfaces.

Claims

Scope of word blue

(1) A metal gasket substrate or other laminated plate used in a multi-cylinder engine is provided with a thickness increasing portion surrounding each combustion chamber hole, and at least a bead formed by surrounding the fuel in the substrate. A metal gasket, wherein one of the sheets is disposed so as to straddle a step formed by the thickness increasing part, and the load of the bead is formed so as to gradually increase from a bolt fastening portion to a periphery of a burning hole.

(2) In the case where the thickness increasing portions of the fuel M holes are close to each other between the respective fuel holes; ^ M holes, the substrate beads are disposed so as to straddle the thickness increasing portions. The metal gasket according to claim 1, wherein the metal gasket is a metal gasket.

(3) When the thickened portions of the fuel holes are spaced apart from each other between the fuel holes, an intermediate plate having a thickness substantially equal to that of the thickened portions is interposed and the outside of each substrate bead is provided. 2. The metal gasket according to claim 1, wherein a wire is provided so as to straddle the middle plate surface and the middle plate step, and an inner wire is provided with an increased front height.

(4) The board bead straddling the thickness increasing portion reduces the load after bolt fastening by increasing the bead width or decreasing the bead height near the tightening bolt hole. 2. The metal gasket according to claim 1, wherein a load after bolt fastening is increased by narrowing a bead width or increasing a bead height between the front lightning holes.

(5) A thickened portion is provided in front of the elastic H-substrate or other laminated plate having a bead surrounding each of the fuel holes of the multi-cylinder engine, on the ^ im hole side. In the metal gasket straddling the cylinder, the projecting shape of the bead in the vicinity of the bolt fastening part for tightening the cylinder head or in front of the entire circumference of the fuel hole ^ m? Ul! The bead dog is formed asymmetrically with the 剕 great part, and the bead dog on the large part is formed into a small curve to increase the panel constant, and the bead on the large part is formed. Gasket, Soto, characterized in that the dog is formed into a large curved or straight-lined dog, and the panel constant is smaller than that of the above-mentioned BJ?

(6) The inside seal line of the bead's fuel hole is formed for each of the fuel holes by passing over the thickness increasing portion, and the outside seal line of the bead's fuel: 7. The metal gasket according to claim 6, wherein the request is to make a tree that passes through the enlarged portion and surrounds each of the fuel holes.

(7) The asymmetric bead shape in the front area in the vicinity of the bolt fastening part changes continuously with respect to the symmetric bead dog between the fuel holes, and changes according to the amount of clearance of the mating surface at each part. 7. The metal gasket according to claim 6, wherein the teaching is that the dog is a dog.