Metal gasket

Abstract: A metal gasket comprising an elastic metal plate(1) including beads(3) formed around cylinder bore holes(2) of a multiple-cylinder engine, wherein each bead(3) comprises an independent bead(9) formed around each hole (2), a common bead(5) between an adjacent pair of holes (2) and junction beads(4) connecting the independent bead(9) and the common bead (5). This metal gasket controls a spring constant at the junction beads(4) to a suitable value by specifying the shape of the junction beads(4), reduces a peak valueof a face-to-face pressure at the junction beads(4), reduces also drop of the face-to-face pressure occurringin the junction beads(4) and at their boundary, and makes uniform the face-to-face pressure in the vicinity of the junction beads(4).

Description: This invention relates to a metal gasket used for sealing a portion between a cylinder head and a cylinder block of a multiple-cylinder engine. In a multiple-cylinder engine, a cylinder head and a cylinder block are coupled to each other by bolts, and a metal gasket is sandwiched between the cylinder head and the cylinder block to prevent the leakage of gas from their fitting surfaces. A known metal gasket includes cylinder bore holes 2 bored in an elastic metal plate 1 and a bead-3 formed around the periphery of each hole 2 as shown in Fig. 1. In this metal gasket, the beads 3 define the seal portion on the fitting surfaces by the clamping force of the bolts, and exhibit an effective sealing function. Recently, a metal gasket has been developed wherein the respective beads 3 join with one another at a junction 4 between two adjacent holes 2 in such a manner as to define a common bead 5 between the holes 2 (e.g. US-A-4,815,750 (corresponding to Japanese Patent Laid-Open No. 210465/1988), Such a metal gasket will be explained with reference to Figs. 9 and 10. In the drawings, like reference numerals will be used to identify like constituents of the metal gasket. Fig. 10 is an enlarged explanatory view showing an example of a junction in a conventional metal gasket. In Fig. 10, each of the two beads 3 is shaped into an arc along the hole 2 at the common bead 5 between the holes 2. A two-dot-chain line represents the center line 6 of the beads, and the center lines 6 of the two beads 3 are in contact with each other at the center of the common bead 5 between the junctions 4. Since the beads 3 have such a shape, the bead width L 1 , L 2 of the non-junction (L 1 = L 2 ) is substantially equal to the bead width L 3 at the center of the common bead 5. In contrast, the bead width L 4 at the junction 4 at which the beads 3 join with each other is about twice the bead width L 1 , L 2 of the non-junction and the bead width L 3 at the common bead 5. As a result, as can be understood from a face-to-face pressure (kgf/mm 2 ) of the bead shown in the graph of Fig. 10 (a linear pressure (kgf/mm) in terms of an analytical value by a finite-element method), the face-to-face pressure drops drastically in the vicinity of a portion at which the bead width greatly changes, that is, near the junction position (regions X and Y encompassed by circles). However, the face-to-face pressure is the reaction that occurs in the beads formed along the holes of the metal gasket when the metal gasket is fitted under the compressed state between a cylinder head and a cylinder block. The drop in face-to-face pressure is particularly remarkable at the portion (region X) near the center of the common bead 5. This drop in face-to-face pressure is believed to result from a small spring constant at the junction 4. In other words, since the ratio of the bead width with respect to the bead height becomes drastically great at the junction position in comparison with the non-junction position, the spring constant becomes small at the junction 4 and for this reason, it is believed that the drop in face-to-face pressure in the vicinity of the junction occurs. As the drop in face-to-face pressure is remarkable at the junction 4 in the metal gasket shown in Fig. 10 as described above, sufficient sealing performance cannot be secured because the face-to-face pressure of the bead affects sealing performance. Fig. 11 is an enlarged explanatory view showing another example of a junction of a conventional metal gasket. The metal gasket shown in Fig. 11 is of an improved type of the metal gasket shown in Fig. 10. In this metal gasket, the beads 3 are formed on the elastic metal plate 1 to perform the sealing function. The holes 2 are bored in the elastic metal plate 1, each bead 3 is so formed as to encompass each hole 2, and the beads 3 join with one another between the adjacent holes 2 and have a linear portion 7 at the center of the common bead 5. In this metal gasket, the bead width of the non-junctions is made progressively smaller towards the junction 4 so that the bead width of the junction 4 of the beads 3 for sealing of each seal portion provided to the elastic metal plate 1 becomes substantially equal to the bead width of the non-junction. In other words, the bead width L 4 of the junction 4 is so shaped as to be substantially equal to the bead width L 1 , L 2 (L 1 = L 2 ) of the non-junction, and the bead width L 4 of the junction 4 and the bead width L 1 , L 2 of the non-junction are shaped into the same size so as to increase the spring constant at the junction 4, and thereby avoid the problem of the drop in sealing pressure at the junction 4 and prevent the face-to-face pressure from becoming non-uniform. As shown in the drawing, this metal gasket certainly has a large spring constant at the junction 4 and the face-to-face pressure does not drop when only the junction 4 is taken into consideration. Nonetheless, according to analytical calculation by the finite-element method, the drop in face-to-face pressure P L of this metal gasket is remarkably great at the boundary between the junction 4 and the non-junction as shown in Fig. 11 and is about 1/2 of the face-to-face pressure P M of the non-junction. Further, since the spring constant of the junction 4 is increased, the face-to-face pressure P MAX of the junction 4 is extremely high, and non-uniformity of the face-to-face pressure is induced. Since this metal gasket has an unbalanced face-to-face pressure state as described above, its sealing performance is not particularly good, and if the spring constant and the face-to-face pressure are increased, undesirable durability problems such as buckling and cracks will rather occur. Therefore, the shape of the beads of the metal gasket shown in Fig. 11 will be examined. Although the bead width L 4 of the junction 4 is the same as the bead width L 1 , L 2 of the non-junction, two center lines 6 of the bead exist in the junction 4 as represented by a two-dot-chain line. Needless to say, the height of the bead 3 does not vary between the junction 4 and the non-junction. Therefore, the sectional shape of the beads 3 at the junction 4 describes two sharp mountains approaching one another in such a way that the bead width of the non-junction decreases progressively towards the junction 4. Since the bead itself is originally very thin and moreover, since the bead width is smaller at the junction 4, the sectional shape of the bead 3 changes complicatedly and drastically at the junction 4. For this reason, the face-to-face pressure becomes extremely great at such a junction 4 and as a reaction, the face-to-face pressure drops drastically on both sides of the junction 4. Moreover, machining of the junction 4 becomes extremely difficult. Amongst other factors, a mold for producing the bead 3 having such a sectional shape which changes in a complicated way is extremely difficult to produce, and practical machining is almost impossible because the production cost is very high. A further development of such a conventional gasket is shown in Japanese Utility Model Publication No. 8678/1989 and corresponds to the definition given by the preamble of appendant claim 1. This gasket is remarkable in the sense that the junction portion of the junction bead is encompassed by an arcuate outer border. The present invention provides a metal gasket including: an elastic metal plate; cylinder bore holes so bored in said elastic metal plate as to be sequentially adjacent to one another; ring-like beads for sealing which are formed around said cylinder bore holes in such a way that one of the surfaces thereof is convex and the other of the surfaces thereof is concave; each of said beads comprising an independent bead formed in a region other than a region between adjacent cylinder bore holes, junction beads formed in regions where the independent beads of adjacent cylinder bore holes join with one another, and a common bead connecting said junction beads and formed in the region between adjacent cylinder bore holes; a bead width of each independent bead being determined by a distance between an inner border and an outer border extending about said cylinder bore holes, and being of substantially the same width around said cylinder bore holes; a bead width of each common bead being determined by a distance between the inner borders of adjacent cylinder bore holes, and being of straight shape; each junction bead being formed by a junction portion encompassed by an arcuate outer border which connects the outer borders of adjacent independent beads with a smooth curve, characterized in that said junction portion is further encompassed by arcuate inner borders which connect the inner borders of adjacent independent beads to the inner borders of said common bead with a smooth curve having a radius of curvature smaller than that of said cylinder bore holes. Preferred embodiments of the present invention will now be described hereinbelow, by way of example only, with reference to the accompanying drawings, in which: Fig. 1 is a schematic plan view showing a metal gasket according to the present invention; Fig. 2 is an enlarged explanatory view showing a bead between the bore holes of a metal gasket according to a first embodiment of the present invention; Fig. 3 is a sectional view taken along a line A - A in Fig. 2; Fig. 4 is an enlarged explanatory view showing a bead between the bore holes of a metal gasket according to a second embodiment of the present invention; Fig. 5 is an enlarged explanatory view of a junction indicated by symbol D in Fig. 4; Fig. 6 is an enlarged explanatory view showing a bead between the bore holes of a metal gasket according to a yet further embodiment of the present invention; Fig. 7 is an enlarged sectional view of a junction taken along a line B - B of Fig. 6; Fig. 8 is an enlarged explanatory view showing a modification to the junction indicated by symbol E in Fig. 6; Fig. 9 is an enlarged sectional view of a junction taken along a line C - C in Fig. 8; Fig. 10 is an enlarged explanatory view showing an example of a junction of a conventional metal gasket; Fig. 11 is an enlarged explanatory view showing another example of a junction of another conventional metal gasket; and Fig. 12 is a comparison graph showing the results of the measurement of the spring constant of each of the metal gaskets shown in Figs. 10 and 11. Fig. 1 is a plan view showing a part of a metal gasket according to the present invention. This metal gasket includes a large number of holes such as cylinder bore holes 2 (hereinafter referred to as the "holes 2"), bolt holes, etc, that are bored in an elastic metal plate 1. A bead 3 is formed around each hole 2. A two-dot-chain line represents a center line 6 of the bead 3. The metal gasket is sandwiched between a cylinder head and a cylinder block and is fastened by fastening bolts. In this instance, the bead 3 undergoes elastic deformation, forms a seal portion between the fitting surfaces, and prevents leakage of gas, oil, and so forth. Fig. 2 is an enlarged explantory view of a portion between the holes 2 of a metal gasket according to a first embodiment of the present invention. In this metal gasket, the bead 3 for sealing, one of the surfaces of which is convex and the other of which is concave, is formed around the periphery of the holes 2 bored in the elastic metal plate 1. The bead 3 comprises independent beads 9 in regions C other than the region between the holes 2, junction beads 4 in regions J at which adjacent independent beads 9 join with one another, and one common bead 5 in a region S between the holes 2. Fig. 2 shows the shape of the bead 3 at the portion between the two adjacent holes 2 in the metal gasket, and dotted lines extending along each hole 2 represent inner and outer borders 8 and 11 which define a width of the bead 3. The common bead 5 is formed into a straight shape having substantially the same width. Each independent bead 9 has substantailly the same bead width as that of the common bead 5, and is shaped into an arc extending along the hole 2. Further, in the region J of the junction beads 4, the bead comprises a smooth arc which has a smaller radius of curvature than that of the independent beads 9, connects the common bead 5 to the independent beads 9, and is shaped into an expanding shape in such a manner that the bead width thereof becomes progressively greater from the common bead 5 toward the independent beads 9 and is separated into two independent beads 9 having the same bead width. In this metal gasket, the bead width L 1 of one independent bead 9, the bead width of L 2 of the other adjacent independent bead 9 and the bead width of L 3 of the common bead 5 are substantially the same (L 1 ≒ L 2 ≒ L 3 ). The bead width L 4 of the junction bead 4, at which the independent beads 9 and the common bead 5 join with each other, becomes progressively greater from the common bead 5 toward the independent beads 9. In other words, the bead width becomes progressively smaller from the two independent beads 9 toward the common bead 5. The sectional shape of the common bead 5 in the section along a line A - A in Fig. 2 in this metal gasket is shown in Fig. 3. The independent beads 9 also have the same sectional shape. Turning back to Fig. 2, a two-dot-chain line represents the center line 6 of each bead. The center line 6 of the one independent bead 9 and the center line 6 of the adjacent other independent bead 9 are shaped into an arc, that is, into a rounded shape, at the junction bead 4, and are connected to the center line 6 of the common bead 5 at this junction point 10. The junction point 10 of the center lines 6 is positioned at the junction bead 4. The length of the perpendiculars drawn from the center lines 6 to the bead border lines on both the inside and outside, that is, to the inner and outer borders 8 and 11, is substantially the same except at the portion in the vicinity of the junction point 10, and the length of these perpendiculars becomes progressively greater in the vicinity of the junction point 10 and reaches a maximum at the junction point 10. The junction bead 4 is defined by an arcuate outer border 15 which connects the outer border 11 of the one independent bead 9 to the outer border 11 of the adjacent other independent bead 9 with a smooth curve (that is, in an arc or a rounded-shape), by an arcuate inner border 16 which connects the inner border 8 of the one independent bead 9 to one of the inner borders 8 of the common bead 5 with an arcuate smooth curve having a radius of curvature smaller than the radius of curvature of the hole 2, and by another arcuate inner border 16 which connects the inner border 8 of the adjacent other independent bead 9 to the other inner border 8 of the common bead 5 with an arcuate smooth curve having a radius of curvature smaller than the radius of curvature of the hole 2. Next, a spring constant of the metal gasket according to the present invention shown in Fig. 2 will be compared with that of a conventional metal gasket. The spring constant shown in Fig. 12 is the result when the common bead 5 is cut out from this metal gasket and is measured. In the diagram, sample A represents the spring constant of the conventional metal gasket shown in Fig. 11, sample B represents the spring constant of the conventional metal gasket shown in Fig. 10, and sample C represents the spring constant of the metal gasket shown in Fig. 2, each with respect to a load. As can be understood from Fig. 12, when the actual measured values of the spring constants in the whole shape are measured, the spring constant of sample C exists between that of sample A and sample B, and no significant difference can be observed. However, when the spring constants in the narrow region J of the junction bead 4 of the bead 3, that is, when 1/2 of the common bead 5 (the portion corresponding to the graph of Fig. 2) inclusive of the junction bead 4 is analyzed and calculated by a finite-element method FEM within the range of an elastic limit, it is found out that differences exist between the analytical values of the spring constants of these metal gaskets. The spring constants are 3.146 x 10 3 kgf/mm for sample A, 1.517 x 10 3 kgf/mm for sample B and 1.582 x 10 3 kgf/mm for sample C. The spring constant of sample C is somewhat greater than that of sample B and is remarkably smaller than that of sample A. When the spring constant of only the junction bead 4 is measured within a practical range of 100 to 150 µm, for example, the spring constant of sample A is high, the spring constant of sample B is low, and the spring constant of sample C exists between those of samples A and B. In this way, these actual measured values exhibit a similar tendency to the calculated values by the analysis of the finite-element method FEM. Next, the face-to-face pressures of the bead, that is, the reaction occurring when the metal gasket is clamped and fitted under the compressed state between a cylinder block and cylinder head, of the metal gasket of the present invention shown in Fig. 2 and the conventional metal gaskets shown in Figs. 10 and 11 will be compared. The peak value of the face-to-face pressure observed at the junction bead 4 of this embodiment is considerably smaller than that of the junction bead of the gasket shown in Fig. 11 and somewhat smaller than that of the junction bead of the gasket shown in Fig. 10. When the drop in face-to-face pressure that occurs across the junction bead 4 is examined, the drop in face-to-face pressure does not occur on the side of the one independent bead 9 as well as on the side of the adjacent other independent bead 9 in the metal gasket of the present invention shown in Fig. 2. The drop in face-to-face pressure on the side of the common bead 5 is also considerably smaller than that in the metal gasket shown in Fig. 11. In other words, it can be understood that the face-to-face pressure of the metal gasket of the present invention shown in Fig. 2 is much more uniform than in the conventional metal gaskets. Fig. 4 is an enlarged view showing the portion between the holes of a metal gasket according to another embodiment of the present invention, and Fig. 5 is an enlarged view of the principal portion of the junction of the metal gasket shown in Fig. 4. The center lines 6 of the independent beads 9 and of the common bead 5 indicated by a two-dot-chain line join with one another at the junction point 10 with an angle of 120°. Since all the adjacent pairs of center lines 6 have an angle of 120° therebetween, the face-to-face pressure can be made to be much more uniform than in the metal gasket shown in Fig. 2. Fig. 6 is an enlarged view showing the portion between the holes of a metal gasket according to still another embodiment of the present invention. The center line 6 of one independent bead 9 connects with that of another adjacent independent bead 9 while describing an arc at the junction 4. Similarly, the center line 6 of the one independent bead 9 and the center line 6 of the common bead 5, and the center line 6 of the adjacent other independent bead 9 and the center line 6 of the common bead 5 connect with one another while describing arcs, respectively. Accordingly, a flat surface 14 encompassed by the three arcuate borders is defined at the junction bead 4. The B-B section which includes this flat surface 14 is shown in Fig. 7. This metal gasket is shaped in such a manner that the length of the perpendiculars drawn from the center lines 6 to the width lines 8 of the bead become substantially the same. This metal gasket, too, can restrict the peak in face-to-face pressure at the junction bead 4 to a considerably low level in the same way as in each of the foregoing embodiments, and can also restrict the drop in face-to-face pressure occurring at the borders on both sides of the junction bead 4. Accordingly, the face-to-face pressure can be made uniform near the junction bead. As shown especially in Figs. 8 and 9, the metal gasket of this embodiment can be provided with a face-to-face pressure regulation recess 13 at the center of the junction portion 17 encompassed by the arcuate outer border 15 and the arcuate inner borders 16 in order to control the face-to-face pressure of the junction bead 4. This face-to-face pressure regulation recess 13 is shaped into a substantially triangular shape, one of the surfaces thereof being convex with the other being concave, and the height is smaller than the thickness of the bead 3. When the face-to-face regulation recess 13 is formed at the center of the flat surface 14, the bead of the junction bead 4 is shaped into a triangular bead comprising bead portions 18 on the three sides, and the bead width of the triangular bead is shaped to a smaller width than the bead width of the independent beads 9 and the common bead 5. When the size of the face-to-face pressure regulation recess 13 is increased, the bead width of the junction bead 4 can be further reduced. When the depth of the face-to-face pressure regulation recess 13 is increased, the three bead portions 18 of the junction bead 4 describe an acute angle, and the face-to-face pressure becomes great. Accordingly, the face-to-face pressure of the junction bead 4 can be regulated to a suitable value by controlling the size and depth of the face-to-face pressure regulation recess 13. In this way, the peak face-to-face pressure at the junction bead 4 of the metal gasket shown in Figs. 8 and 9 can be suitably reduced to a smaller value than that in the conventional metal gaskets by forming the face-to-face pressure regulation recess 13 at the junction bead 4 in the metal gasket as shown in Figs. 8 and 9, and the face-to-face pressure of the independent beads 9 can be brought close to that of the common bead 5 without lowering drastically the face-to-face pressures at the boundary between the junction bead 4 and the independent beads 9 and at the boundary between the junction bead 4 and the common bead 5. In this way, sealing performance of the metal gasket can be improved by controlling the face-to-face pressure uniformly around the entire periphery of a hole 2. It is an aim of the preferred embodiments of the present invention to provide an economical and high reliability metal gasket which includes beads formed around cylinder bore holes bored in an elastic metal plate in such a way as not to reduce bead width at junction beads and to minimize the change in sectional shape of the beads, but to permit a smooth change, which brings a spring constant of the junction close to a spring constant of a non-junction comprising a common bead and an independent bead, which minimizes a peak value in face-to-face pressure at the junction as well as the drop in face-to-face pressure occurring at the boundary between the junctions and the non-junction, thus making uniform the face-to-face pressure in the vicinity of the junction, securing durability and preventing the occurrence of buckling and cracks. In a preferred embodiment of the present invention described above, a face-to-face pressure regulation recess is formed at the center of the junction portion of the junction beads so as to control the face-to-face pressure of the beads. Therefore, since the spring constant at the junction beads can be set to a suitable constant by the size of the face-to-face pressure regulation recess, a load stress on the junction beads is prevented from becoming excessively great, neither buckling nor cracks occur from the junction beads, and durability can be improved. In a preferred embodiment of the present invention, the peak value of the spring constant of the junction beads is reduced and is brought close to the spring constant of the common bead, and the drop in the spring constant on both sides of the junction beads is restricted and is brought close to the spring constants of the independent beads and the common bead. In a preferred embodiment of the present invention, the peak value of the face-to-face pressure of the junction beads is reduced and is brought close to the face-to-face pressure of the common bead, and the drop in face-to-face pressure of the regions on both sides of the junction beads is restricted and is brought close to the face-to-face pressures of the independent beads and the common bead. In the present invention, the common bead and the independent beads are connected in the region of the junction beads by a smooth curve with a radius of curvature smaller than that of the independent beads. Therefore, the portion having a large bead width can be made smaller than in the conventional metal gasket shown in Fig. 10, the spring constant of the junction beads can be made greater than in the metal gasket shown in Fig. 10, and the drop in face-to-face pressure is not so great as in the metal gasket shown in Fig. 10. Further, in the metal gasket of the present invention the spring constant is smaller than in the metal gasket shown in Fig. 11 and the peak value of the face-to-face pressure at the junction beads can be restricted to a lower value. At the same time, the drop in face-to-face pressure occuring at the boundary between the junction beads, the independent beads and the common bead can be minimized, and the face-to-face pressure in the vicinity of the junction beads can be made uniform. In a preferred embodiment of the present invention, a triangular portion encompassed by the center lines of the three beads is formed in the region of the junction beads and the length of the perpendiculars from these center lines to the boundary of the beads is substantially the same. Therefore, the portion having a large ratio of bead width to bead height is smaller than in the metal gasket shown in Fig. 10, so that the spring constant at the junction portions is greater than in the metal gasket shown in Fig. 10. In other words, the drop in face-to-face pressure in this metal gasket is not much greater than in the metal gasket shown in Fig. 10. Since the metal gasket is shaped in such a way that the length of the perpendiculars drawn from the center lines of the beads to the boundary of the beads becomes substantially constant, the change in bead width of the beads at the junction beads is small and the sectional shapes of the beads do not change significantly. Accordingly, the spring constant becomes smaller in this metal gasket than in the metal gasket shown in Fig. 11, and the peak value in face-to-face value becomes smaller. Because the peak value in face-to-face pressure at the junction beads can be limited to a considerably small value in this way and at the same time, because the drop in face-to-face pressure at the borders on both sides of the junction beads can be limited likewise to a lower value, the face-to-face pressure in the vicinity of the junction beads can be made uniform. Moreover, since the metal gasket of the present invention has beads shaped such that the change in bead width is small and the sectional shapes of the beads do not change significantly, the beads need not be reduced in size at the junction beads unlike the conventional metal gasket, the production of the mold becomes easy and simple, and the production cost can be reduced. Since the drop in face-to-face pressure occurring at the junction beads and on both sides of the junction beads can be restricted to a considerably low level in this metal gasket, the face-to-face pressure on both sides of the junction beads can be secured and the face-to-face pressure at the junction beads does not reach an unnecessary high level. Accordingly, the face-to-face pressure in the vicinity of the junction beads can be made uniform, and stable sealing performance can be secured.

Claims: A metal gasket including: an elastic metal plate (1); cylinder bore holes (2) so bored in said elastic metal plate (1) as to be sequentially adjacent to one another; ring-like beads (3) for sealing which are formed around said cylinder bore holes (2) in such a way that one of the surfaces thereof is convex and the other of the surfaces thereof is concave; each of said beads (3) comprising an independent bead (9) formed in a region other than a region between adjacent cylinder bore holes (2), junction beads (4) formed in regions where the independent beads (9) of adjacent cylinder bore holes (2) join with one another, and a common bead (5) connecting said junction beads (4) and formed in the region between adjacent cylinder bore holes (2) ; a bead width of each independent bead (9) being determined by a distance between an inner border (8) and an outer border (11) extending about said cylinder bore holes (2), and being of substantially the same width around said cylinder bore holes (2); a bead width of each common bead (5) being determined by a distance between the inner borders (8) of adjacent cylinder bore holes (2), and being of straight shape; each junction bead (4) being formed by a junction portion (17) encompassed by an arcuate outer border (15) which connects the outer borders (11) of adjacent independent beads (9) with a smooth curve, characterized in that said junction portion (17) is further encompassed by arcuate inner borders (16) which connect the inner borders (8) of adjacent independent beads (9) to the inner borders (8) of said common bead (5) with a smooth curve having a radius of curvature smaller than that of said cylinder bore holes (2). A metal gasket according to claim 1, wherein said common bead (5) and said independent beads (9) are of substantially the same width. A metal gasket according to claim 1 or 2, wherein said arcuate outer border (15) comprises an arc having the radius of curvature thereof on the outer side of said outer borders (11) and on the imaginary extension of the center line of said common bead (5). A metal gasket according to any one of claims 1 to 3, wherein said junction beads (4) are formed in such a way that the width thereof becomes progressively greater from said common bead (5) toward said independent beads (9). A metal gasket according to any one of claims 1 to 4, wherein a junction point of the center lines of said beads (3) is positioned at said junction bead (4), the length of the perpendiculars from said center lines to said inner and outer borders (8, 11) of said beads (3) is substantially the same other than at a portion in the vicinity of said junction point where said perpendiculars become progressively longer, and said beads (3) are formed so that the length of said perpendiculars reaches the maximum at said junction point. A metal gasket according to any one of claims 1 to 4, wherein a triangular flat portion (14) encompassed by the center lines of said junction beads (4) is formed at said junction beads (4), and the length of the perpendiculars from said center lines to the outer borders of said beads (3) is substantially the same. A metal gasket according to any one of claims 1 to 6, wherein a face-to-face pressure regulation recess (13) is formed at the center of said junction portion (17) so as to control the face-to-face pressure of said junction bead (4). A metal gasket according to claim 7, wherein said face-to-face pressure regulation recess (13) is triangular. A metal gasket according to claim 7 or 8, wherein the size and depth of said face-to-face pressure regulation recess (13) are regulated so as to regulate the face-to-face pressure of said junction beads (4).

Inventors: INOUE KUNITOSHI, KUBOUCHI KENJI, INOUE, KUNITOSHI, KUBOUCHI, KENJI
Applicants: NIPPON GASKET KK, NIPPON GASKET COMPANY LTD.
Application year: 1993
Main classification: F16J15
IPC codes: F16J15