WO2013011124A1

WO2013011124A1 - Seal system

Info

Publication number: WO2013011124A1
Application number: PCT/EP2012/064284
Authority: WO
Inventors: Ahmet ORUC; Kurt Höhe; Hans Waldvogel; Oliver Claus
Original assignee: Reinz-Dichtungs-Gmbh
Priority date: 2011-07-20
Filing date: 2012-07-20
Publication date: 2013-01-24
Also published as: DE202011103439U1

Abstract

The invention relates to a seal system consisting of a first component, a second component, and at least one fluid through-opening that extends in both components, in particular a through-opening for hot combustion gases of internal combustion engines and the corresponding flat metal seal. The invention relates to a seal system consisting of a first component (2), a second component (3), and at least one fluid through-opening (22) that extends in both components, in particular a through-opening for hot combustion gases of internal combustion engines and the corresponding flat metal seal.

Description

sealing system

The invention relates to a sealing system consisting of a first component and a second component and at least one in both components extending

Fluid passage opening, in particular a passage opening for hot

Combustion gases of internal combustion engines and the associated metallic

Flat seal.

In the prior art, on the one hand substantially flat overlying metallic gaskets are used between the two components. The

Fluid passage openings are surrounded by elastic sealing elements, usually formed directly in the sheet metal layer corrugations. These may be in the main body of force, i. experience full compression or, either by shoring in a groove or by introducing a deformation-limiting element in the seal in the

Force shunt be brought so that they can be pressed only to the depth of the groove or the height of the deformation limiting element. This ensures that the bead is biased substantially only within its elastic range and thus it does not leave this discharge even. Due to the full-surface shoring these seals always have through holes for fastening means, i. They are bolted between the two components to be sealed against each other. A disadvantage arises from the large material consumption, since the seal extends over a fairly large area, compared with the area encompassing the actual sealing lines. For components having multiple fluid passage openings, a significant problem of this type of seal results from different ones

Thermal expansion coefficient of the components to be sealed and the seal. When cold starting in winter, for example, at -20 ° C, the system should be just as tight as after prolonged operation with operating temperatures of over 800 ° C or turbochargers even at over 1000 ° C. This is counter to large, connecting the through holes sections of material that experience a different extent than the components to be sealed. The positions of the fluid passage openings are thus shifted from each other and there are tensions and / or leaks. In addition, the adaptation to the

Sealing gap movements strongly limited. Further, from the prior art inserted tubes with circumferential imprints are known. These seal different fluid passage openings independently. But they are very complex in their production and often have precision problems. Especially the production of radial embossing is very delicate and often lead to small deviations in the component or seal dimensions to large sealing problems. Furthermore, the seals are exposed over their entire length to the hot and aggressive fluids, mostly fuel gases. To avoid corrosion, therefore, extremely high-quality and therefore expensive materials must be used. Both components to be sealed move to different degrees, so occurs in mehrflutigen

Transition destroys sealing tubes, as they can not follow the movement.

In addition, c, <and ε-ring profile seals are used in grooves for sealing such sealing systems. However, they are very expensive to produce. For a seamless production, a multi-stage manufacturing process is necessary, in which the material is also very much reshaped. Alternatively, a production of a ring to be closed to the sheet metal is possible, but also results in more intense

Post-processing always an inhomogeneity at the junction, which can act as a predetermined breaking point and also cause leaks. In addition, these c, <and ε rings may be due to the necessary final

Rolling process can only be produced in a circular design.

The object of the invention is accordingly to provide a sealing system available that ensures a durable sealing effect, reproducible with little effort and can be experienced by the passage of aggressive and hot media wear only to a small extent.

The solution of this problem is achieved with the sealing system according to claim 1 and the use of the sealing system according to claim 25. Preferred embodiments are described in the subclaims.

The invention thus relates to a sealing system consisting of a first component, a second component and a metallic flat gasket with at least one

Fluid passage opening extending into both components or even through both components. At least one of the components has a groove that the Surrounds fluid passage opening and in which the metallic gasket is received. At least radially outside the groove, the first and second components come to rest on their common extension area. The seal itself is therefore only in the groove. The seal can consist of several layers or even only one layer. Unlike the seals inserted in grooves of the prior art, so for example rings with C or ε-profile, the sealing surfaces of the layers of the metallic gasket used in the sealing system according to the invention in a projection in a plane parallel to the contact surface of the first and second component or in each case in the plain of the groove bottom in each case in one layer. Optionally, only the two edges of the seal may deviate therefrom. Thus, the sealing surfaces, in particular between their edges, no Umfalzungen or recesses so that they simply by forming,

can be made in particular by stamping and stamping from a flat sheet metal. For this reason, the seal is referred to as a metallic flat gasket, even if it does not have a smooth course even after the deformation. The position or layers of the seal is / are not flat, but has / point in

Radial direction depending on viewing direction on a climb or descent. This approach or descent is greater in the unpressed state of the seal than the groove depth, so that the seal unfolds in the compressed state down (groove bottom) and upwards (further component) a sealing effect. The sealing effect is retained in an elastic form, since the arrival or descent between the top and bottom point a Bbzwungsungsbzw. In a particular embodiment, this is the arrival or descent superimposed on a waveform.

The rise or descent thus has on both sides of the deflection or the kink each a different strong increase or decrease, in particular different rise / fall angles, on. On both sides of the deflection / kink, the rise / fall at least partially advantageously each with a constant slope, for example, over> 10% of the groove width and / or with a slope between 30 ° and 85 °.

A groove in the context of this invention must not be closed on both sides laterally, the term groove also includes a recess limited only on one side. The groove may also be formed in only one of the components or formed by both components. In the unpressed state, the seal has a height which is greater than the groove depth. The So seal over or ensures that the components are spaced apart without being clamped together. In the assembled state, this results in the bias of the seal. Overall, the seal extends annularly, so

encircling, in the area of the groove.

In an advantageous embodiment of the invention, the radially inner and radially outer ends of the seal point towards a virtual center plane of the seal, i. a plane parallel to the contact surface of the first and second component, which runs halfway up the seal. This reduces on the one hand when handling the seal the

Risk of injury and on the other hand ensures that the seal is not or only barely buried in the surfaces of the components to be sealed.

It is also advantageous if the metallic gasket of the

Sealing system, optionally with the exception of the inner edge and / or the outer edge of the seal, has no section perpendicular to the above

Center plane or to the level of the contact surface extends. This causes the gasket to be easily deformed over its entire radial course.

Optionally, at the inner edge and / or at the outer edge of the flat gasket, sections may extend vertically, which extend over <40%, advantageously <25%, advantageously <15% of the height of the gasket in the unpressed state or in the compressed state.

The groove itself may be formed in only one of the components or formed by two components. The groove in which the seal is received, can directly adjoin the fluid passage opening, so that it is open to this. However, this has the disadvantage that the seal is fully exposed to the hot and aggressive gases. To prevent this, it is advantageous if the groove is delimited both on its radially outer and on its radially inner side of at least one of the components, so that hot and aggressive gases can reach the seal only to a small extent.

In addition, the two-sided limitation of the groove also ensures an improved support between the two components. This can even lead to a clawing of the edges of the

Flat seal with the adjacent groove edges and thus lead to a further improved seal. If a spring of the counter component protrudes into the groove, then the effective Groove height reduced. When considering the groove height, only the effective groove height counts in this case.

Furthermore, it is advantageous for the durability of the sealing system or the metallic flat gasket when the flat gasket is made of a material that is less susceptible to corrosion. Here are mainly steel, especially stainless steel, as well

To name nickel-base alloys. As a special form of the nickel-based alloys, so-called superalloys are particularly suitable, which are especially creeping and

are fatigue-resistant, since they do not soften at high temperatures, but are hardened by solid solution formation and precipitations. One example is Inconel® alloy 718. Among the stainless steels, austenitic ones are preferred, for example 1.4828, 1.4301 or 1.4310.

Thus, the seal in the compressed state has sufficient alternative possibilities, it is preferred that they are in the unpressed state in projection in the plane of the

Contact surface of the first and second component has a radial extent which is less than the radial extent of the groove. Most of the seal is designed so that the deeper penetrating into the groove edge of the seal itself adjacent to the adjacent edge of the groove or from this edge tabs, preferably at least two, more preferably at least three tabs, adjacent to this edge of the groove. At the other edge of the seal thus preferably results in a distance from the groove wall.

A radially overlying or descending the seal overlapping waveform preferably has at least two waves, so that at least two wave troughs and two wave crests arise, which can act as sealing lines in a strong compressed state of the seal. The waves do not necessarily have to be uniform, but may in particular have different height and width. Furthermore, distances between the waves are possible. Instead of two troughs and two wave crests, the superposition can only create a true trough and a true wave crest, between which several inflection points result as uneven troughs or mountains.

With respect to the orientation of the rise or fall of the seal, it may be advantageous if the radially inner side of the seal in the non-compressed state from the Nut protrudes, so that it already acts as a barrier in the compressed state, before the sealed gases can impinge on more outer surface portions of the seal.

For an optimum sealing effect, it is particularly preferred if the metallic flat gasket in the unpressed state has a height which exceeds by more than 250 μιη, preferably by more than 500 μιη via the groove. The seal thus has a total of at least 250 μιη, preferably more than 500 μιη greater total height than the groove. This ensures a sufficient preload as well as a deformation in the

elastic range. Based on the groove depth of the supernatant of the unpressed seal is at least 17%, preferably at least 25%.

The radial extent of the seal is usually limited by the space available for the formation of the groove. Typical radial extensions are between 2 and 5 mm. In large engines, such as marine engines, more space is available, so that the radial extent of the seal can also be larger.

Also, the extent of the arrival and / or descent of the metallic flat gasket relative to the plane of the contact surface of the components influences the springback and thus the sealing effect of the metallic flat gasket. The upper limit of the maximum increase of the real waveform results in tool technology about 85 °. For a good sealing effect, the maximum increase in the real waveform should be at least 30 °. Within the range of 30 to 85 °, shallower angles are preferred since they provide the

Increase springback potential of the seal. A real waveform should be understood to mean the actually existing shape of the seal or a section through it, ie the sum of the rise and the superimposed wave is considered.

Unlike some seals to be inserted in grooves of the prior art, the metallic flat gasket has no radially extending slots, as they are without

Overuse of the starting material can be punched and stamped from a metal sheet. In projection into the contact plane of the two components results in a

Ring shape with continuous course from the inner edge to the outer edge.

In its simplest embodiment, the seal of the sealing system according to the invention is carried out substantially axially symmetrical. For the automated Assembly is preferably at least one mark attached, which allows the detection of top and bottom. Even more preferred is when the seal

Positioning tabs, as these can then be used for this detection. The marking or the positioning tabs are usually sufficient for a correct automated recording and alignment of the seals for assembly, so that a transport as bulk material is easily possible. The positioning tabs do not count towards the sealing surface, so they can be folded differently than the other areas of the flat gasket.

On the other hand, the metallic flat gasket of the invention

Sealing system, the possibility not to manufacture the seal, as usual in the art, circular, but also allows the production of other, optionally self-contained seal geometries, in particular ovals, other elongated structures or other rounded shapes. Not only does the outer geometry of the seal obtain this shape, but also preferably the courses of the respective peaks and valleys.

It is manufacturing technology advantageous if the metallic gasket consists only of a single layer in which the radial arrival or descent is a deflection / bending point superimposed in such a way that the gasket layer in projection in a plane parallel to the contact surface of the two components to be sealed against each other only consists of a single layer, so neither Umfalzungen nor has recesses.

To increase the sealing potential, however, it is advantageous if the metallic flat gasket consists of several layers, wherein in each of these layers of the radial approach or descent is superimposed by a circumferential deflection / bending line. Again, each of the layers is in projection in a plane parallel to the contact surface of the two components to be sealed against each other only one layer at a time. None of the layers thus has Umfalzungen or recesses.

On the one hand, the multi-layered gasket may be designed so that the adjacent or all layers have the same direction of emergence or descent and, preferably, extend substantially parallel to one another. It is on the one hand possible to produce the layers independently. If the layers are made with the same neutral fiber, only the flanks of the wave structure of the adjacent sealing layers to each other, while there is usually no contact between the layers in the region of wave crests and valleys, since the adjacent surfaces have a different course. On the other hand, it is possible, in particular when the layers are cut together and reshaped, to be substantially parallel to one another. This is especially true at

Bimetallic solutions, ie in metal composites with two layers of different metal, in particular of metals with different thermal expansion coefficients, advantageous. With this arrangement, the spring force of the seal increases.

On the other hand, the multi-layered gasket can be designed such that the layers are essentially mirror-symmetrical to one another. The gasket layers in this way form series-connected elastic elements whose springback reinforce each other. Advantageously, the gasket layers lie flat on one another in their edge region. For this purpose, it is preferred if both gasket layers have mutually parallel edge regions. For a simple installation of the seal, it is advantageous if the gasket layers not only rest on each other, but are connected to each other. If the seal has positioning tabs, it is advantageous if these are also used for the layer connection. In this case, in addition to a crimping the tab of a layer around the tab of the other and a compound by means

Spot welding done. If the gasket layers, however, within their

Sealing area, i. not connected in the region of the tabs, provide in particular cohesive connections, preferably welding. In this case, it is preferred if the layers are welded tightly around one another, for example by means of laser welding.

For the sealing system according to the invention is that the height and width ratios and angles within the seal circumferentially may be substantially constant or may vary to adapt to the conditions in the components to be sealed.

The invention will be explained in more detail with reference to drawings. These drawings are merely illustrative of preferred embodiments without the invention being limited to them. Individual elements of individual examples can also represent advantageous developments of the invention, independently of the further features of the respective example. In the figures, the same or like reference numerals refer to like or similar parts, but they are not necessarily explicitly mentioned in the description of each embodiment to avoid repetition.

In the drawings show schematically:

Figure 1: a first component of a sealing system according to the invention; Figure 2: in two sub-figures 2-a and 2-b, a sealing system of the state of

Technology;

Figure 3: the sealing system according to the invention in four sub-figures; Figure 4: in two sub-figures, two different embodiments of a metallic flat gasket of an inventive

Sealing system;

FIGS. 5 and 6 show two oblique views of sections through metallic flat gaskets of a sealing system according to the invention;

FIGS. 7 to 10 are sectional views through metallic flat gaskets of sealing systems according to the invention;

Figure 11: a plan view of a metallic gasket of a

sealing system according to the invention with oval geometry;

Figures 12 and 13: sectional views of two-ply gaskets of the invention

Sealing system;

Figure 14 is a sectional view of a seal of the invention

Sealing system; and

FIG. 15: a sectional view through a sealing system according to the invention.

Figure 1 shows as the first component of a sealing system according to the invention a flange 2 with two fluid passage openings 22. The two fluid passage openings 22 are each and independently surrounded by an annular groove 20 and a groove 20 against the fluid passage opening 22 shielding collar 21.

In addition, the flange has a plurality of through holes 23 for fastening means on. The edge portions surrounding the through holes 23 for fastening means are not visible in the straight plan view other than surrounding the fluid passage openings edge portions 24, since the latter in the present example relative to the plane of the flange 2 kinked, ie with a deviating from 90 ° angle, while the Through openings 23 for fastening means have an angle of 90 °.

In Figure 2, in sub-figures 2-a and 2-b, a sealing system of the prior art both in a sectional view of the insulated seal 101 and in a

Sectional view of the entire sealing system with both adjacent to the seal 101 components 2,3 in the unpressed state. The seal 101 here consists of two interlocking C-shaped ring profiles 101a, 101b made of sheet metal. In the illustrated unpressed state, the seal is at a height HU on the

Groove height above. The through openings for fastening means run here in a different sectional plane than that represented by the components 2, 3. Such C-rings can be prepared in principle with two different methods. If a round, smooth sheet metal section is formed into a C-ring in several deep-drawing steps, then after a final rolling step, a seam-free C-ring is created that meets the technical requirements. However, the multi-stage production process is so complicated that the associated costs for a mass-produced article are unacceptable. The

Production from a subsequently closed to the ring plate is first

inexpensive. But it remains a connection point, which interrupts an otherwise homogeneous circumferential sealing line and also has a greater roughness. The

Junction can therefore lead to sealing problems. Various methods have been used to counteract this, including the combination of two C-rings shown here with staggered seams. The more effort is spent on smoothing the joint, the higher the cost of the seal. But even with great effort, it is not possible to make the joint unrecognizable.

In Figure 3, in three sub-figures 3-a to 3-c are each an inventive

Sealing system shown in cross section. The fourth sub-figure 3-d shows a magnified excerpt from FIG. 3-b. The sealing system consists of two components 2 and 3 to be sealed against each other, a groove 20 formed by at least one of these components, and a seal 1 received in this groove 20. The seal consists of this from a single metallic sheet metal layer and surrounds the fluid passage opening 22 annular. The seal 1 is wave-shaped. Thus, it also has at least one point to whose two sides rise or fall of the seal are different. The embodiments of the seal 1 shown in Figures 3-a and 3-b differ only in that the groove 20 for receiving the seal in Figure 3-b is formed directly in the component 2, while the groove in Figure 3-a thereby shows that the gradations 20a and 30a are offset in the components 2 and 3 against each other. Again, the passageways for fasteners lie in planes other than the cut one.

Figure 3-c differs from Figure 3-b in that in Figure 3-c, the assembled state is shown with a compressed seal 1, while Figure 3-b demonstrates the state after Aufeinanderfügen but before tightening the screws. In Figure 3-c it is illustrated that the marked, non-terminal wave crest S as well as the marked, non-terminal wave t also in the compressed state of the seal 1 does not come to rest on the surfaces 25, 35 of the components 2, 3. So they do not form any other sealing lines, but the wavy overall shape gives the seal 1 optimal

Spring properties.

It is essential to the invention that the single-layer seal 1 has a profile which rises outward over its radial extension and which, in the present example, has a waveform overlaid on it. The overall increase in the non-compressed state is greater than the groove depth HN, as can be easily seen in FIG. The enlarged detail B from FIG. 3-b in FIG. 3-d makes it clear that the respective end sections 12, 13 point into the interior of the seal or in the direction of the opposite support plane of the seal. It is also clearly visible in the illustrated section that when the flat gasket 1 is e.g. is projected from above onto a plane parallel to the plane of the contact surface 32 of the two components 2 and 3, always only one sheet metal section is present. The seal thus has no folded areas or radial recesses.

This is also apparent from the plan view in Figure 4-a. It can also be seen there that the seal 1 can have a relatively strongly structured middle region 14 between two less structured end sections 12, 13. The embodiment of Figure 4-b differs from that of Figure 4-a by the additionally existing retaining lugs 19. These project from the inner edge of the seal and have a rounded shape on. The size of the retaining lugs 19 is advantageously chosen so that the retaining lugs rest on the edge of the groove 20 facing the fluid passage opening. They are preferably very narrow and are slightly bent when inserted into the groove 20, so that they have a slight bias against the groove wall and are thus secured against falling out. The number of retaining lugs can vary between two and six, with three retaining lugs being preferred. The retaining lugs 19 are then provided on the inner edge of the seal 1 when in the unpressed state of

Sealing system of the inner edge of the seal in the groove 20 is immersed. In contrast, only the outer edge of the seal 1 immersed in the groove 20 in the unpressed state, the retaining lugs are preferably provided on the outer edge.

Figures 5 and 6 illustrate again typical radial and circumferential courses of the seals of the sealing system according to the invention. The end sections 12, 13 always point in the direction of the seal center plane. On the one hand this prevents burial, but on the other hand also allows to fully exploit the elastic effect of the respective terminal wave crest or valley.

FIGS. 7 to 10 illustrate typical sections through seals 1, shown in isolation, of the sealing system according to the invention. Figures 7 and 8 each have two wave peaks Sl, S2 and troughs Tl, T2. In Figure 9 there are in addition to real mountains and valleys S, T near the end portions 12, 13 nor turning points W as deflection or

Kinks. In contrast, the embodiment according to FIG. 10 is distinguished by three wave peaks and valleys S1, S2, S3, T1, T2, T3. All seals have an increase from the inside to the outside. Rise angles are referred to here as a, descent angle β. On the other hand, if the radial direction of the seal increases from inside to outside, then α denotes a descent angle and β denotes a rise angle.

Thus, FIG. 7 shows the metallic flat gasket of a sealing system according to the invention, such as one of those shown in FIG. The seal has an overall height HG. It is called despite its non-planar course as a metallic gasket, since it is formed only by stamping and stamping from a flat sheet. The increase of the seal over its radial extent ER is HA. In this case, a waveform having two wave crests Sl, S2 and wave troughs T1, T2 is superimposed on the rising profile. While the two ascending sections each have a rise angle α of 60-70 °, the intermediate portion only slightly decreases, namely with an angle ß of 20-25 °. The rise angles are here more than twice as large as the descent angle. In any section of the seal, an angle of 90 ° relative to a plane parallel to the center plane M is reached or even exceeded. So there is no folded area. It is also clear that the two

Have end portions 12, 13 to the center plane M of the seal 1 at half the height of the total height HG.

The embodiment of Figure 8 differs from that of Figure 7, especially by even steeper angle of rise a, which are here between 70 and 80 °. Also, the angle ß of the descending section is slightly steeper at 28 ° than in the previous example. Again, the slope angles α are more than twice as large as the descent angle β. While the descending angle of the outer end portion 13 is significantly steeper than before and also passes as the angle β, the increasing angle of the inner end portion 12 is substantially less than that of the previous example and also the angle a.

In the example of FIG. 9, only one wave peak S and one wave valley T can be recognized. In between are two significant inflection points W1, W2, between which a relatively long, straight section A extends obliquely upward. So there is no effective descending range. The wave superimposed on the rise is not periodically structured here. The angles al and a2 are almost identical here and are between 78 and 81 °. Much steeper angles can not be produced by tools in a single embossing step. The maximum possible angle is about 85 °. The long stretch between the turning points, however, increases with an angle of about 23 °. Again, the end portions 12, 13 to the midplane M.

The metallic flat gasket shown in section in Figure 10 has over the previous embodiments, a larger number of wave periods. This results in each case three wave peaks Sl, S2, S3 and valleys Tl, T2, T3. The angles of rise α here are all between 60 and 75 °, whereby the angle increases minimally from the inside to the outside: α3 <a2 <al. The two descent angles β are essentially identical here and amount to approximately 22 °. Again, the end portions 12, 13 to the center plane M of the seal. Due to the greater number of waves, the embodiment of Figure 10 has a greater elasticity than the previous examples. However, due to its larger radial extension ER, it also requires more installation space, ie a wider groove. Whether such a large number of waves can actually be used depends on the individual case.

All cross sections 7 to 10 of metallic flat gaskets of the sealing system according to the invention show that they have no over the rise and the waveform beyond profiling. There is no intended variation of the sheet thickness, neither as shown in the radial direction of extension, nor circulating.

Figure 11 demonstrates on the basis of a plan view of a seal with an oval base body that it is possible without considerable additional effort to produce deviating from the circular shape seal shapes for sealing systems of the invention, after all, the seal is only punched out and embossed. The shape usually depends on the shape of the groove. It is preferred if the inner and outer edges are concentric with each other and also the course of the wave peaks and valleys is concentric therewith.

Figures 12 and 13 show sectional views of two-ply seals 1 of the sealing system according to the invention. Both illustrated seals each consist of two layers la, lb. In FIG. 12, in both partial figures, the two layers 1a, 1b act together in such a way that they extend essentially parallel to one another, wherein they each have a respective increase from the inner edge 13 to the outer edge 12. However, in FIG. 12a, the seals only touch each other in their flank region F1, F2, F3; the wave peaks and valleys are spaced apart from each other in the unpressed state. When pressing the seal this distance is utilized and the gasket layers la, lb approach each other. This two-layer embodiment is characterized by a higher pressure than the single-layer embodiments described above. It is also possible in this way to use two thinner sheets instead of one thick sheet. In Figure 12-b, the two metal layers la, lb are directly adjacent to each other, for example, because they were already made of a double lying sheet metal. This variant is particularly preferred in bimetal solutions in which two metals interact with different thermal expansion coefficients. Figure 13 illustrates a two-layered embodiment of the seal, in which the layers la, lb, unlike in Figure 12 are not parallel to each other, but essentially mirror-inverted. Adjacent to its inner edge 13, both gasket layers 1a, 1b have a straight region 40, in which both layers run parallel to one another and rest on one another. Further in the direction of the outer edge 12, the two gasket layers la, lb move away from each other. The upper layer la increases in total, while the lower layer lb undergoes a descent. This results in the upper layer la two wave peaks Sla, S2a with a wave trough Tla in between and in the lower layer lb two troughs Tlb, T2b with a wave mountain Slb in between. For ease of handling of the seal 1, the two layers la, lb not only on each other, but are connected to each other by means of welding. It is advantageous for the tightness of the sealing system when the weld 50 is circumferentially sealed. The combination of the two gasket layers results in a total series connection and thus a gain of the spring action.

For both the embodiments of Figure 12 and that of Figure 13, the invention is not limited to single and double-layer seals, but in principle may include more layers.

For all embodiments shown, the height and width ratios as well as angles within the seal 1 can be substantially constant all around or can vary to adapt to the conditions in the components 2, 3.

Figure 14 shows another seal 1 according to the invention. This is similar to that of Figure 9 formed, but only a turning point W is provided. Adjacent to this inflection point W, the pitch of the seal 1 has different pitch angles. Between the edge 13 and the inflection point W, which can also be referred to as a kink or bend, the pitch angle oti is 29 °. In the further course of the seal between the inflection point W and the end 12 of the seal 1, the pitch angle a _{2 is} 83 °. a ₂ is thus considerably larger than oii. In this embodiment of the seal 1 according to the invention, the pitch over large parts of the seal adjacent to the inflection point W is kept constant in each case. Figure 15 shows a further embodiment of the seal according to the invention in a sealing system according to the invention, wherein the seal 1 between two components 2 and 3 is inserted into a groove 22 and seals there. This seal is similar to that in FIG. 3d, the profile of the section from the inside to the outside in FIG. 15 substantially corresponding to the profile of the section of FIG. 3d from the outside to the inside.

The seal 1 is here designed so that it digs into the material of the component 2 during compression between the groove bottom of the groove 22 and the surface of the component 3 at its end 13 and thereby an additional sealing line is formed.

Claims

claims

Sealing system containing or consisting of

a first component (2) and a second component (3)

wherein the first component (2) and the second component (3) are arranged on one another at a common contact surface and have a fluid passage opening (22) which projects into the first and second component (2, 3),

an annular groove (20) in the first and / or second component which surrounds the fluid passage opening (22) and adjoins or protrudes beyond the contact surface (32) of the first and second components (2, 3), the first and second ones Component (2, 3) in the area outside the groove (20) come to lie on each other,

marked by

a metallic flat gasket (1), which extends annularly in the groove (20), wherein the metallic flat gasket (1) at least one metallic layer (la, lb) and each of their layers (la, lb) in the non-compressed or compressed Condition in a projection in a plane parallel to the contact surface (32) of the first and second component (2, 3) or in the plane of Nutgrund at each point, optionally with the exception of its inner and / or outer edge, only one layer, and

the metallic flat gasket has a total or each of its layers (la, lb) in the unpressed state in the radial direction a rise or fall (HA) greater than the groove depth (HN), which has a deflection or kink between the top and bottom point.

Sealing system according to the preceding claim, characterized in that the metallic flat gasket (1), optionally with the exception of its inner edge and / or outer edge, has no portion which is perpendicular to the contact surface of the first and second component (2, 3).

Sealing system according to the preceding claim, characterized in that extending at the inner edge and / or at the outer edge of the flat gasket extending portions perpendicular to the contact surface of the first and second component (2,3), over <40%, advantageously <25% , advantageously <15% of the height of the gasket in the unpressed state or in the compressed state extend.

Sealing system according to one of the preceding claims, characterized in that the flat gasket has a rise or fall, which is superimposed on a waveform.

Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket is supported with its uppermost point against the upper component and with its lowest point against the sole of the groove and is resiliently pressed between these two points.

Sealing system according to one of the preceding claims, characterized in that the inner and the outer end portion (12, 13) of the metallic flat gasket (1) with respect to their height respectively to the center plane (M) of the seal (1) show.

Sealing system according to one of the preceding claims, characterized in that the groove (20) on both its radially inner and on its radially outer side of at least one of the components (2, 3) is limited.

8. Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket (1) in the non-compressed state in projection into the contact surface of the first and second component has a radial extent (ER), which is less than the radial extent of the groove Is.

9. Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket has a total of (1) or each of their layers (la, lb) over its radial extent (ER) at least two waves.

10. Sealing system according to one of claims 1 to 8, characterized in that the metallic flat gasket overall (1) or each of their layers (la, lb) over their radial extent (ER) only a wave crest (S) and a wave trough (T) has and between either a steady arrival or a steady descent, wherein the rising or falling angles (a, ß) change over the continuous range.

11. Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket (1) in the non-compressed state has a height (HG) which is at least 250 μιη, preferably at least 500 μιη greater than the groove height (HN) ,

12. Sealing system according to one of the preceding claims, characterized in that the radial extent (ER) of the metallic flat gasket (1) in the unpressed state in projection in the plane of the contact surface (32) is between 2 and 5 mm.

13. Sealing system according to one of the preceding claims, characterized in that the maximum increase of the flat gasket, relative to the contact surface between the two components in the un compressed state or in the compressed state between 30 ° and 85 °, advantageously between 80 ° and 85 °.

14. Sealing system according to one of the preceding claims, characterized in that the increase on both sides of the deflection or kink has different slope angles relative to the contact surface.

15. Sealing system according to the preceding claim, characterized in that the increase on both sides of the deflection or the kink in each case over> 10%, advantageously> 20%, advantageously-> 30% of the groove width is constant.

16. Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket (1) is axially symmetrical with respect to its outer shape and optionally, in particular, has no radial slots.

17. Sealing system according to one of the preceding claims, characterized in that along the circumference of the metallic flat gasket (1) at least one, extending in the radial direction weld is arranged.

18. Sealing system according to one of the preceding claims, character- ized in that the metallic flat gasket (1) at its

Inner and / or outer edge at least two positioning devices, in particular at least two, preferably three tabs (19).

19. Sealing system according to one of the preceding claims, character- ized in that the metallic flat gasket (1) with respect to its outer shape, in particular with respect to its outer edge and / or its inner edge, a geometry deviating from the circular shape.

Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket (1) consists of at least two layers (la, lb), wherein the layers (la, lb) in the radial direction each have either an increase or decrease superimposed on the waveform and touch each other at least in the flank area (Fl, F2, F3).

Sealing system according to one of claims 1 to 19, characterized in that the metallic flat gasket (1) consists of at least two layers (la, lb), wherein the radial course of two adjacent layers is substantially mirror-inverted to each other and the layers in the unpressed state only touching in a circumferential area (40) and preferably in this area connected to each other, in particular welded together (50) or by folding the positioning tabs (19) are connected to positioning tabs of another layer.

Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket (1) consists of at least two layers (la, lb), wherein at least two of the layers (la, lb) consist of different material, in particular of metals with different thermal expansion coefficients or these contain.

Sealing system according to one of claims 1 to 19, characterized in that the metallic flat gasket (1) consists of exactly one layer.

24. Sealing system according to one of the preceding claims, characterized in that the metallic flat gasket (1) as a whole or one of its layers (la, lb) consists of a steel, in particular a stainless steel, or a nickel-based alloy, in particular a so-called superalloy, or these contain.

25. Use of a sealing system according to one of the preceding claims, in the exhaust gas region of an internal combustion engine of a motor vehicle.