DE102009022313A1 - Connecting system for conduits, fittings or assemblies, particularly carbon dioxide guiding system, comprises coupling piece, particularly housing part, and another coupling piece, particularly plug-in part with shank - Google Patents

Abstract

The connecting system comprises a coupling piece (1), particularly a housing part, and another coupling piece (2), particularly a plug-in part with a shank (5) inserted into a retainer opening (6) of the former coupling piece along the axial direction. The geometry and the material of the peripheral seals, and the geometry of a groove (4) are aligned on top of each other. The O-ring (31) is made of hydrogenated nitrile butadiene rubber, ethylene propylene diene monomer rubber, or fluoroelastomer rubber.

Description

The The present invention relates to a connection system for Lines, fittings or aggregates used to guide a increased with respect to a comparison pressure Pressure applied to fluids are determined, in particular for Carbon dioxide leading systems comprising a first coupling part, as a housing part, along an axis in a receiving opening the first coupling part with a shaft insertable second Coupling part, such as a plug part, and at least two peripheral seals, in the axial direction one behind the other in at least one circumferentially in one of the two coupling parts formed groove are arranged and in the assembly and in the operating state, a gap of the receiving opening Close and a peripheral seal on the Side of the increased pressure in a first groove area arranged O-ring and the other peripheral seal on the side of the comparison pressure is in a second groove portion arranged molding ring.

Such a connection system is known from the European patent EP 1 052 443 B1 or from its German translation DE 600 07 219 T2 known. These documents describe a device for limiting the leakage for a refrigeration cycle through which a refrigerant flows, the refrigeration cycle having an air-connected pipe connection part to which pipes are connected. This known device for limiting leakage presents a technical solution which does justice to the contradictory sealing requirements with respect to low permeability and prevention of explosive decompression, which depends on a characteristic called blistering resistance in the documents.

A in such connection systems initially from the point of view a low leakage desirable low permeability a seal leads to an undesirable high tendency to form bubbles and thus increased Risk of occurrence of explosive decompression. A worthwhile high blistering resistance of the gasket, through which This can be avoided, on the other hand leads to undesirable high permeability and thus leakage of coolant. To limit the leakage of coolant into the air, therefore comprises the known leakage limiting device - instead of one, designated as leakage limiting element, seal with each average gas permeability and blistering resistance - two formed as seals leakage limiting elements: a first Leakage limiting element, the air side in the pipe connection part is arranged, and a second leakage limiting element on the coolant side is arranged in the pipe connection part. The first element has a gas permeability and a Blistering resistance, each less than those of the second leakage limiting element are. According to one Variety of embodiments are as leakage limiting elements O-rings are provided, each arranged in two consecutive Grooves are arranged and have different cord diameters can. This should at least by a strong compression an O-ring, which, however, disadvantageously increased with Plug forces is connected, a large permeation be generated. According to one embodiment the known device for limiting the leakage, considered as generic The first leakage-limiting element may be on the side of the elevated pressure arranged O-ring and the second Leakage limiting element on the side of the comparison pressure be arranged molding ring with rectangular cross section. Thereby should be achieved that when the pressure of the coolant is increased, the O-ring is prevented from being locally deform in the axial direction. Specifically, there is a form ring shown with square cross section, but not like the other embodiments of the leakage limiting elements by a strong compression an enlarged Permeation length generated.

One Consequently, the problem with this connection system is that either no optimal permeation length through the leakage limiting elements created or characterized by the presence of two circumferential seals, one of which is excessively compressed, disadvantageously - because of the friction of each peripheral seal on the wall and because of the compression of the seal body during insertion - the insertion forces that occur during assembly increase. The known connection system can therefore with regard to a ratio of permeation length to the used for the compression of the leakage limiting elements Insertion forces are not considered optimal.

Of the present invention is based on the object, a connection system of the type mentioned above for pipes, fittings or To improve aggregates in such a way that under warranty a high level of installation friendliness in the production of the coupling connection and a high reliability and low leakage the latter also under environmental influences, like temperature and Pressure and preferably also changing chemical-physical media character of the fluid, can be maintained while the above overcome disadvantages mentioned.

According to the invention achieves this for a system of that kind by that the geometry and / or the material of the circumferential seals as well the geometry of the groove are coordinated such that at an insertion of the second hitch be part in the receiving opening the first coupling part along the axis a maximum insertion force when inserting the form ring by a maximum of 20 percent of a maximum Insertion force when inserting the O-ring deviates.

By the invention will affect both qualitatively and quantitatively taken on the insertion forces. It is through the mutual Matching the groove geometry and the geometries of the peripheral seals or the material of the peripheral seals possible, on the one hand with optimally low insertion forces the contradictory Sealing requirements for low permeability and prevention of explosive decompression, but also a high functionality of the system among the to secure a wide variety of operating conditions. Please note that the insertion forces depend on one Plug-in path when inserting the second coupling part in the first Clutch part are variable. This dependence The plug-in forces from the plug-in path can be determined by curves be expressed. In these curves Basically, it comes in principle when plugging an increase in insertion force from a zero value at the beginning of insertion to a non-zero final value. In each case, two local Go through maxima. These maxima are due to the deformation of the Circumferential seals when entering the receiving opening caused and by the geometry of the seals and their material properties, for example determines the Shore hardness. One each behind one Maximum setting lower, partially constant in areas Value of insertion force becomes almost exclusive instead caused by the friction on the wall of the receiving opening.

In Preferred embodiment of the invention can be provided that the geometry and / or the material of the circumferential seals as well the geometry of the groove are coordinated such that at a Inserting the second coupling part in the receiving opening of the first coupling part along the axis, the maximum insertion force when inserting the O-ring not larger than, in particular about the same size as the maximum insertion force when plugging of the molding ring.

in the The invention can be achieved by designing a ratio a major axial dimension to a major radial dimension of Mold ring, wherein the mold ring in the unpressed state an axial Major dimension that is larger than its Radial main dimension is, advantageously, an optimal relation between the perpendicular to the axial direction extending cross-sectional area the deformed circumferential seal and the permeation length be set. It is particularly advantageous if the Ratio of the axial main dimension to the radial main dimension greater than 1.2, preferably larger as 2.0.

Of Furthermore, the invention advantageously allows a device for Achieving an optimal sealing effect required groove fill, which is a quotient of an in-groove portion of the compressed, radial cross section of the circumferential seals and the cross-sectional area the groove can be calculated to optimally adjust what is in the known leakage control device is completely disregarded. This can be done according to the invention without this is due to the two circumferential seals during assembly Increase occurring insertion forces.

For this may be provided in particular that exclusively the second groove area by a geometric design of his Cross-section in a seat portion and in a compensation section is subdivided with a smaller cross-section than the seat portion, wherein the mold ring in a preassembled state prior to insertion of the second coupling part in the first coupling part exclusively is located in the seat portion and in the assembled state, the seating area completely filled and in the compensation section protrudes. This is a possibility according to the invention the Groove geometry and the geometries of the peripheral seals optimized to coordinate with each other.

there Strengthens in that only the atmosphere assigned groove area by said shaping in a seat portion and an expansion section, and the refrigerant facing groove area solely by dimensioning the groove volume - ie without an additionally geometrically defined expansion section, d. H. the seating area is identical to the expansion area - dimensioned, through the use of two differently shaped seals occurring synergistic effect. At the same time can by a in this design possible optimization of the insertion forces the ease of installation of the system can be increased.

The total permeation length of the fluid through the seal, through the axial longitudinal extent the deformed seal between the two coupling parts is determined, according to the invention divided into a permeation through the O-ring and in a Permeationslänge through the mold ring, which can be coordinated. Furthermore, within the molding ring there is the advantageous possibility of optimizing the permeation length by designing the seat section, the compensation section and the properties of the molding ring itself. With regard to the known state of the art, it is therefore advantageous to provide further basic geometric geometric variables as freely selectable design variables of the system. Based on these circumstances, the cross-sectional area of the components of the deformed circumferential seal can be kept small and the mean permeation length large at a given system pressure and operating time to achieve a small amount of leakage. A compensation of manufacturing tolerances of the parts to be joined can take place.

In particular, the connection system according to the invention is predestined for the use of carbon dioxide as a refrigerant in an air conditioning system which, in comparison with the pressures usual for halogen-containing refrigerants, have increased pressures and temperatures in the heat exchange processes. Thus, for the occurring during operation of a CO ₂ air conditioning pressure an upper level of about 160 bar and a lower level of about 35 bar characteristic.

One Fill level, which is a quotient of one in each section or in the whole groove portion of the compressed, radial Cross-section and the cross-sectional area of this section or the groove can be calculated is in the seat section while in mounted state equal to 1 or 100 percent and preferably larger as the degree of filling of the expansion section. This preferred Training can be beneficial especially about it In addition, so also mean that in the assembly and operating state taking into account the possible thermal expansion of the mold ring as a quotient of a lying in the compensation section Proportion of the compressed, radial cross-section and the cross-sectional area the degree of compensation calculated smaller is 1 or 100 percent.

in the second groove area is due to the invention to each other coordinated dimensioning of the first groove area and seat portion, Compensation portion of the second groove portion and the mold ring thus formed a space for the form of ring, him so absorbs that at a volume increase of the Circumferential seal, as in the operating state at one opposite the room temperature elevated temperature or by swelling under the influence of the fluid, or at a deformation the circumferential seal, as under the influence of the pre-pressing force or the increased pressure occurs, a destruction of the Seal and extrusion into the gap to be sealed avoided can be. The compensation space can thus function on the one hand the formation of an escape space for receiving the deformed volume part fulfill the circumferential seal, but on the other hand, the Function of creating an additional space for recording an enlarged volume of the peripheral seal.

The O-ring protects the mold ring from any aggressive attack by fluids, which may be, for example, refrigerants such as R134a, CO ₂ or HFO1234yf, or by their components, such as a refrigerator oil. The O-ring may thus preferably have a higher resistance, in particular a higher thermal or chemical resistance, to the fluid, such as an oil or an oil-refrigerant mixture, than the molding ring. As a result, the aging of the mold ring is advantageously reduced.

By the inventive dimensioning of the molding ring and the geometric design of the intended for him groove portion can advantageously also have a contact surface, which serves as an interface of the O-ring to the fluid in the direction of the fluid points, in the operating state be optimally kept small.

Further advantageous design features of the invention are in the subclaims and the following description.

Based Several preferred embodiments will be described below the invention will be explained in more detail. Showing:

1 in a longitudinal section, a representation of a detail of a connection system according to the invention in a first embodiment,

2 and 3 in longitudinal section, representations of the parts of a connection system according to the invention in a second embodiment, wherein the in 2 shown coupling part is already pre-assembled with circumferential seals,

4 in longitudinal section, an illustration of the connection system according to the invention in the second embodiment, wherein the in 2 and 3 parts are completely assembled,

5 in a longitudinal section, an illustration of the parts of a connection system according to the invention in a third embodiment, wherein a second coupling part, which can be inserted in a first coupling part, is already pre-assembled with peripheral seals,

6 in longitudinal section, an illustration of the connection system according to the invention in the third embodiment, wherein the in 5 parts are completely assembled,

7 a qualitative diagrammatic representation of the dependence of the insertion forces that occur when inserting a second coupling part in a first coupling part in a connection system according to the invention in dependence on the plug, compared to the corresponding ratios in two non-inventive connection systems,

8th a quantitative diagrammatic representation of the dependence of the insertion forces, which can characteristically occur when inserting a second coupling part into a first coupling part in various embodiments of a connection system according to the invention as a function of the plug-in distance,

9 in a longitudinally sectioned half section, a representation of a peripheral part with pre-assembled coupling part of the connection system according to the invention in a fourth embodiment,

10 in a longitudinally sectioned half section, a representation of a peripheral part with pre-assembled coupling part of the connection system according to the invention in a fifth embodiment,

11 in a longitudinally sectioned half section, a representation of a peripheral part with pre-assembled coupling part of the connection system according to the invention in a sixth embodiment,

12 in a longitudinally sectioned half section, a representation of the (final) mounting state of a connection system according to the invention in a seventh embodiment,

13 in a longitudinally sectioned half section, an illustration of an intermediate mounting state of a connection system according to the invention in an eighth embodiment,

14 in a longitudinally sectioned half section, an illustration of the (end) mounting state of a connection system according to the invention of the eighth embodiment,

15 in a longitudinally sectioned half section, an illustration of the coupling part of the connection system according to the invention, in which the other coupling part is inserted, in an embodiment, the 3 and 4 corresponds,

16 in a longitudinally sectioned half section, a representation of the mounting state of a connection system according to the invention in a ninth embodiment,

17 in a longitudinally sectioned half section, a representation of the mounting state of a connection system according to the invention in a tenth embodiment,

18 in a longitudinally sectioned half section, an illustration of the mounting state of a connection system according to the invention in an eleventh embodiment,

19 in a longitudinally sectioned partial section, a representation of a pre-assembled with peripheral seals coupling part of the connection system according to the invention in a twelfth embodiment,

20 consisting of the subfigures 20a to 20c , in each case in a longitudinally sectioned partial section, various possible shapes of the second slot region of a connection system according to the invention,

21 in a longitudinally sectioned partial section, an illustration of a provided with peripheral seals coupling part of the connection system according to the invention in the operating state in a further embodiment.

In the various figures of the drawing, the same and corresponding parts are always provided with the same reference numerals and will therefore be described below in the following generally only once. In the statements according to 9 to 21 are not all in for clarity 1 to 6 designated reference numerals. The statements according to 9 to 21 With the specific training described in each case for the specific embodiment, each have the same constructive basic structure according to the invention as the embodiments according to FIG 1 to 6 ,

An important difference in 1 shown first embodiment of the invention over the in 2 to 4 shown second and opposite the in 5 and 6 In the first embodiment shown, the O-ring and the forming ring in the first embodiment are seated in groove areas of a single groove formed according to the present invention, whereas according to the second and third embodiments, each of the first groove area and the second groove area is defined by a radial groove circumferential web are separated from each other and thereby each form a separate first groove and a separate second groove.

While in 1 a specific type of connection system according to the invention is not specified relate 2 to 4 on a line connection and 5 and 6 on a block connector.

1 to 6 illustrate the following basic structural design of a connection system according to the invention for lines, fittings or aggregates, in particular for carbon dioxide-carrying systems, which are intended to guide a pressurized with respect to a reference pressure p ₂ pressure p ₁ fluid:
An inventive connection system comprises a first coupling part 1 as a housing part (for the second embodiment as a single part in 3 shown), along an axis XX in a receiving opening 6 of the first coupling part 1 with a shaft 5 insertable second coupling part 2 as a plug part (for the second version as a single part in 2 shown), and two circumferential seals 31 . 32 in the axial direction XX in succession in at least one circumference in one of the two coupling parts 1 . 2 trained groove 4 are arranged. The circumferential seals close 31 . 32 under deformation and generation of a radial pre-pressing force FV in the assembled state ( 4 . 6 ) and in the operating state ( 1 ) a gap 7 the receiving opening 6 , A circumferential seal 31 is one on the side of the increased pressure p ₁ in a first groove area 41 arranged O-ring 31 , and the other circumferential seal 32 is one on the side of the comparative pressure p ₂ in a second groove area 42 arranged form ring 32 ,

It is characteristic of the invention that the geometry and / or the material of the peripheral seals 31 . 32 as well as the geometry of the groove 4 are matched to one another such that when inserting the second coupling part 2 in the receiving opening 6 of the first coupling part 1 along the axis XX a maximum insertion force M2 _31/32 when inserting the form ring 32 by a maximum of 20 percent of the maximum insertion force M1 _31/32 when inserting the O-ring ( 31 ), as will be described below with reference to 7 and 8th is explained.

It is provided in particular, as this first from the representations of the unpressed circumferential seals 31 . 32 in 2 and 5 it can be seen that the cross section Q _{32 of} the molding ring 32 in the unpressed state has a major axial dimension B ₃₂ , which is longer than a radial main dimension s ₃₂ . In particular, a ratio of the axial main dimension B ₃₂ , which is in the cases shown by a line width of the molding ring 32 is the major radial dimension s ₃₂ , which is a cord thickness measured radially, greater than 1.2, and preferably greater than 2.0. In contrast to the prior art described above, a large permeation length does not have to be generated by strong compression during the insertion process, so that an optimally large ratio of permeation length to that for the compression of the peripheral seals 31 . 32 expires plug forces.

It is provided that the second groove area 42 - And preferably only this - in a seat portion S and in a compensation section K is divided with a smaller cross-section Q _K as the cross-section Q _{S of} the seat portion S, wherein the mold ring 32 in a preassembled condition ( 2 . 5 ) before inserting the two th coupling part 2 in the first coupling part 1 exclusively in the seat portion S and in the assembly and operating state ( 1 . 4 . 6 ) Completes the seat portion S completely and protrudes into the compensation section K. The seat portion S has a length L _S and the compensation section K has a length L _K. Optionally, even in the preassembled state, the seat portion S can be completely filled. As a result, advantageously, the mold ring 32 do not slip during assembly.

The presence of the compensation section K contributes to the execution of the molding ring 32 Bill that is larger than that of the O-ring 31 , Consequently, volume enlargements due to swelling under pressure and thermal expansion are thus larger than in the case of the O-ring 31 and can by expansion of the molding ring 32 be compensated in the compensation section K without appreciable increase in the radially directed surface pressure.

An axial length L _{42 of} the second groove area 42 can - as in 1 . 2 and 5 shown - preferably larger than an axial length L _{41 of} the first groove portion 41 be (only in 1 and 2 designated). An axial cross-sectional area Q _{41 of} the first groove area 41 may preferably be smaller than an axial cross-sectional area Q _{42 of} the second groove area 42 be (in 1 and 4 designated). A maximum depth T _{41 of} the first groove area 41 may preferably be smaller than a maximum depth T _{42 of} the second groove area 42 be (in 1 and 2 designated).

In the first to third embodiments, it is provided that the molding ring 32 in the preassembled state, in the assembly and in the operating state with a first axially directed contact surface FA ₃₂ on a groove flank 42a is applied, which lies axially opposite the compensation portion K and the seat portion S limited.

The second groove area 42 can here - as shown - in particular be designed geometrically such that the cross section Q _{K of} the compensation section K, at least over a defined axial length L _Ka away, in the direction Z of the axial insertion of a coupling part 2 in the receiving opening 6 of the other coupling part 1 seen in longitudinal section in the radial direction steadily and / or abruptly reduced relative to the cross-section Q _{S of} the seat portion S. This advantageously leads to the fact that - even during assembly or later in a swelling of the seal in the operating state - the permeation length increases abruptly and disproportionately through the seal. Here, in the first three embodiments in the compensation section K, at least over the defined axial length L _Ka away, a flat or curved, in particular convexly curved, in the direction Z of the axial insertion of a coupling part 2 in the receiving opening 6 the other coupling part radially outwardly extending inclined surface 42b educated.

A compensation for the change in the geometry of the molding ring 32 can, as in 1 shown with the additional radial compensation volume V _R , both in the axial and in the radial direction, and the compensation section K may consist of several partial compensation volumes.

With a view to optimizing the matching of the geometries of the molding ring 32 and second groove area 42 In particular, it may be provided that in the assembly and operating state, preferably taking into account the possible thermal expansion of the molding ring 32 , as a quotient of a lying in the compensation section K portion of the compressed radial cross-section AR _32K and the cross-sectional area Q _{K of} the compensation section K calculated filling degree FG is less than 1 or 100 percent. In this case, a degree of filling FG, which results as a quotient of a portion of the compressed, radial cross-section AR _32S lying in the seat portion S and the cross-sectional area Q _{S of} the seat portion K, can be equal to 1 or 100 percent. A filling level FG of the entire second groove area 42 , which is the quotient of the whole, in the second groove area 42 lying compressed radial cross-section AR _{32 of} the mold ring 32 and the total cross-sectional area Q ₄₂ (sum of Q _S and Q _K ) of the groove area 42 may preferably be less than 1 or 100 percent.

Like the first groove area 41 prefers a flat groove base 41a can also - at least partially - the compensation section K of the second groove area 42 and / or in particular - as shown - the seat portion S of the second groove area 42 a flat groove bottom 42c exhibit.

In the first embodiment of the invention, the O-ring is located 31 in the preassembled state, in the assembly and in the operating state with a first axially directed contact surface FA ₃₁ at a contact surface FB ₃₂ facing it of the mold ring 32 at. On the other side is the O-ring 31 at least in the assembled state with a second axially directed contact surface FB ₃₁ at a groove flank lying in the insertion direction Z. 41b at.

As already mentioned, it is provided according to the second and third embodiments of the invention that the first groove area 41 and the second groove area 42 by a radially circumferential web 8th are separated from each other and thereby each a separate first groove 41 and a separate second groove 42 form. The O-ring 31 is there in the preassembled state and in the assembled state with its first axially directed contact surface FA ₃₁ on a groove flank 41c the first groove 41 on, passing through the radial circumferential web 8th is formed. On the other side is the O-ring 31 - As in the first embodiment - at least in the assembled state with his second axially directed contact surface FB ₃₁ at the lying in the insertion Z groove flank 41b at.

With regard to an optimal coordination of the geometries of the groove areas 41 . 42 or the grooves 41 for the O-ring and the form ring 32 successive may be provided that a ratio of the length L ₄₁ to the maximum depth T _{41 of} the first groove portion 41 or the first groove 41 is greater than a ratio of the length L ₄₂ to the maximum depth T _{42 of} the second groove area 42 or the second groove 42 , In this case, the ratio of the length L ₄₁ to the maximum depth T _{41 of} the first groove portion 41 or the first groove 41 in the range of 1 to 5, and preferably at 3.5. The ratio of the length L ₄₂ to the maximum depth T _{42 of} the second groove area 42 or the second groove 42 may be in the range of 0.3 to 0.9, and preferably 0.5.

As for the design of the peripheral seals 31 . 32 is concerned, as in 2 and 5 denoted by reference numeral, a cord thickness s _{31 of} the O-ring 31 smaller than a radially measured cord thickness s _{32 of} the molding ring 32 while in the compressed state ( 1 . 4 and 6 ) an axial length L _{31 of} the O-ring 31 smaller than an axial length L _{32 of} the molding ring 32 is. In the compressed state, it is preferred - based on the axis XX - a mean ring diameter DM _{31 of} the O-ring 31 smaller than a mean ring diameter DM _{32 of} the molding ring 32 be. These middle ring diameter DM ₃₁ , DM ₃₂ are in each case as a mutual distance of the centers of the cross sections Q ₃₁ , Q _{32 of} the circumferential seals 31 . 32 determined. Such average ring diameter DM ₃₁ , DM ₃₂ are exemplary in the embodiments in 9 . 11 . 12 . 19 . 20 and 21 shown.

In mounting and operating conditions, the radial pre-pressing force FV _{31 of} the O-ring should be 31 not greater than, preferably the same size as the radial pre-pressing force FV _{32 of} the molding ring 32 be.

Due to the pre-pressing forces FV ₃₁ , FV _{32 of} the O-ring 31 and the form ring 32 Among other things, depending on how strong each one peripheral seal 31 . 32 is deformed or how much space according to size and geometric design for this deformation is available, in addition to a contact length, over which the peripheral seal 31 . 32 each on the walls of the coupling parts 1 . 2 is applied, also affects the insertion forces FS, when inserting the second coupling part 2 in the first coupling part 1 occur in a connection system according to the invention in dependence on the plug-X. The respective ratio of the insertion force FS to the orthogonal standing on the insertion force FS Vorpresskraft FV is the coefficient of friction μ.

The insertion forces FS are also of the nominal diameter of the receiving opening 6 dependent. For nominal diameters of 12 mm, the maximum insertion forces M1, M2 are expected in the range of 80 N to 100 N. For larger nominal diameters or even for small nominal diameters, but at the pressure range relevant for CO ₂ (p ₁ = 10 bar to 180 bar) , larger maximum insertion forces M1, M2 occur, which can reach more than 100 N and 120 N. Such maximum insertion forces M1, M2 can be avoided according to the invention, in particular as described below with reference to FIG 8th will be shown.

At first, however, goes out 7 show how the insertion forces FS can be qualitatively influenced by the invention. 7 shows the changes in the insertion forces FS as a function of a plug-in X when inserting the second coupling part 2 in the first coupling part 1 in comparison between a connection system according to the invention (curve 31/32 ) and two non-inventive connection systems (curves 31/31 and 32/32 ).

The curve name 31/31 indicates that in the first non-inventive connection system two O-ring seals 31 combined with each other while the curve name 32/32 expresses that in the second connection system not according to the invention two form-ring seals 32 arranged one behind the other.

All Curves initially show an increase in principle the insertion force FS from a value zero at the beginning of insertion to a non-zero final value E.

When plugging in two local maxima are run through, which are designated M1 and M2 and in the drawing additionally - as well as the end values E - in each case by the indices 31/31 . 31/32 . 32/32 the corresponding curve are marked. The maxima M1, M2 are determined by the deformation of the peripheral seals 31 . 32 when entering the receiving opening 6 causes, while in each case behind a maximum M1, M2 setting lower, partially constant value SW remains (also in each case according to the arrangement of the peripheral seals 31 . 32 indicated) of the insertion force FS in particular exclusively by the friction on the wall of the receiving opening 6 is caused.

The end value E _{31/31 of} the combination of two O-rings 31 is the lowest and adjusts itself the most via the plug-in X. The end value E _{32/32 of} the combination of two form rings 32 is highest and adjusts itself via the plug-in X last. The final value E _{31/32 of} the combination _{according to} the invention is in between. The maxima M1 _31/31 M1 _31/32 , M2 _31/31 , which correspond to the respective plug of the O-ring 31 are both a steeper increase in insertion force FS before the maximum, as well as a steeper drop to the maximum than the maxima M1 _32/32 , M2 _31/32 and M2 _32/32 , which on the respective plug of the molding ring 32 are attributed. This is associated with the fact that in the compressed state, the axial length L _{31 of} the O-ring 31 smaller than an axial length L _{32 of} the molding ring 32 is.

Because both in the combination of two O-rings 31 as well as in the combination according to the invention, in which on the shaft 5 seen in the insertion direction Z front an O-ring 31 This first sits in the receiving opening 6 passes, the curve of the two combinations is first at passage of the first maximum M1 to the entrance of the second circumferential seal - either the second O-ring 31 or according to the invention the molding ring 32 - congruent. When the second maximum M2 is set, the curves then start to deviate from one another, with the respective _maxima M2 _31/31 and M2 _31/32 reaching approximately the same peak value, but this only occurs after a longer plug-in path X in the combination according to the invention.

When combining two molding rings 32 If the first maximum M1 _{32/32 occurs} at a longer plug-in distance X than the maximum M1 for the other two combinations. The situation is similar with the second maximum M2 _32/32 . This occurs only with a longer plug-X X than in a combination according to the invention.

• – Bei einem Einstecken des zweiten Kupplungsteils 2 in die Aufnahmeöffnung 6 des ersten Kupplungsteils 1 entlang der Achse X-X sollte die maximale Steckkraft M1_31/32 beim Stecken des O-Rings 31 bevorzugt nicht größer als, insbesondere etwa genauso groß wie die maximale Steckkraft M2_31/32 beim Stecken des Formrings 32 sein.
• – Bei einem solchen Einstecken weicht die maximale Steckkraft M2_31/32 beim Stecken des Formrings 32 erfindungsgemäß um maximal 20 Prozent von der maximalen Steckkraft M1_31/32 beim Stecken des O-Rings 31 ab.
• – Bei einem solchen Einstecken kann die maximale Steckkraft M2_31/32 beim Stecken des Formrings 32 und die maximalen Steckkraft M1_31/32 beim Stecken des O-Rings 31 jeweils im Bereich von 40 bis 100 N liegen.
• – Beim Einstecken entlang der Achse X-X sollte bevorzugt eine Stecklänge SL₃₁, über die die Steckkraft FS größer als die Hälfte der maximalen Steckkraft M1_31/32 ist, beim Stecken des O-Rings 31 im Bereich von 1 bis 2 mm liegen.
• – Beim Einstecken entlang der Achse X-X sollte bevorzugt eine Stecklänge SL₃₂, über die die Steckkraft FS größer als die Hälfte der maximalen Steckkraft M2_31/32 ist, beim Stecken des Formrings 32 im Bereich von 3 bis 5 mm liegen.
• – Beim Einstecken entlang der Achse X-X kann die Stecklänge SL₃₂, über die die Steckkraft FS größer als die Hälfte der maximalen Steckkraft M1, M2 ist, beim Stecken des Formrings 32 bevorzugt 2 bis 4 Mal so groß sein wie die entsprechende Stecklänge SL₃₁ beim Stecken des O-Rings 31.

The different in 8th quantitatively represented for the invention, qualitatively with those in 7 matching curves of the dependence of the insertion force FS of the plug-in route, illustrate the following technical features:

• - When inserting the second coupling part 2 in the receiving opening 6 of the first coupling part 1 Along the axis XX, the maximum insertion force M1 _31/32 when inserting the O-ring 31 preferably not larger than, in particular approximately the same size as the maximum insertion force M2 _31/32 when inserting the molding ring 32 be.
• - In such a plugging the maximum insertion force M2 _31/32 deviates when inserting the form ring 32 according to the invention by a maximum of 20 percent of the maximum insertion force M1 _31/32 when inserting the O-ring 31 from.
• - With such an insertion, the maximum insertion force M2 _31/32 when inserting the form ring 32 and the maximum insertion force M1 _31/32 when inserting the O-ring 31 each in the range of 40 to 100 N.
• - When inserting along the axis XX should preferably a length SL ₃₁ , over which the insertion force FS is greater than half of the maximum insertion force M1 _31/32 , when inserting the O-ring 31 be in the range of 1 to 2 mm.
• - When inserting along the axis XX should preferably a length SL ₃₂ , over which the insertion force FS is greater than half of the maximum insertion force M2 _31/32 , when inserting the mold ring 32 be in the range of 3 to 5 mm.
• - When inserting along the axis XX, the insertion length SL ₃₂ , over which the insertion force FS is greater than half of the maximum insertion force M1, M2, when inserting the molding ring 32 preferably 2 to 4 times larger than the corresponding length SL ₃₁ when inserting the O-ring 31 ,

These features, in particular the fact that the maximum insertion forces M1 and M2 are about the same size, a technical solution for the conflict of objectives is brought about, which results from the fact that the peripheral seals 31 . 32 on the one hand strongly pressed, so compressed, to be, which is connected to high maximum insertion forces M1, M2, on the other hand, the maximum insertion forces M1, M2 should be small, so that the ease of installation is guaranteed.

So z. B. for in 8th Curves shown a preferred target value for both maxima M1 _31/32 , M2 _{31/32 of} the insertion force FS are consistent at about 90 N. When the insertion force FS for the O-ring 31 already set to a maximum M1 _31/32 of about 90 N, would result in a lower tightness when the molding ring 32 to a lower maximum insertion force M2 _31/32 , z. B. to 50 N, would be set. Such an attitude is therefore not desirable.

As in the explanation of the curves on the basis of 7 has been executed, the first peripheral seal ( 8th : O-ring 31 ), which is pressed, a base value SW ready, which of the mentioned, in each case behind the first maximum M1 lying low, partially constant value of the remaining Insertion force FS is. This value SW - or SW _31/32 according to 8th For example, it may preferably be about 15N. To this base value, the component of the insertion force FS added by the second peripheral seal ( 8th Image: Form ring 32 ) arises. The peak value M2 should therefore not exceed the peak value M1 taking into account the base value SW. If the maxima M1 and M2 at about the same value, z. B. of 90 N, so this means that, taking into account the base value SW, the component of the insertion force FS, by the second peripheral seal ( 8th Image: Form ring 32 ) should be about 20% smaller than the value of the maximum insertion force M1 of the first peripheral seal ( 8th : O-ring 31 ). This is like 7 shows, only then the case, provided first the O-ring 31 is mounted. A first assembled form ring 32 creates a comparatively higher base value (cf. 7 : SW _32/32 ). This would be the same size of the circumferential seals 31 . 32 and their associated groove sections 41 . 42 a reverse assembly sequence - so first the form ring 32 , then the O-ring 31 - not practical as a technical solution to the above-mentioned conflict of goals.

The dimensioning of the lengths SL ₃₁ and SL ₃₂ serves the purpose of setting the maximum insertion forces M1, M2 approximately the same size, wherein the above-mentioned ratio of the lengths SL ₃₁ and SL ₃₂ with respect to both circumferential seals 31 . 32 as an optimum in terms of simultaneously highest possible tightness and the lowest possible maximum insertion force M1, M2 results. The dimensioning takes into account the fact that due to the inventive dimensioning of the molding ring 32 due to the larger compressed peripheral surface a higher frictional base value SW sets than the O-ring 31 , If the length SL _{31 is} increased, the base amount and the subsequent form ring increases 32 can either be pressed only less strong, or it must be a shortening of length SL ₃₂ .

Preferred properties of the O-ring 31 and the form ring 32 are shown in Table 1 below. Table 1: Properties of the peripheral seals 31, 32 property O-ring 31 mold ring 32 material EPDM HNBR, EPDM, FKM Shore hardness 75-95 prefers 85 75-85 prefers 75

According to its functions, oil and lubricants from the molding ring 32 To keep away and protect the latter from explosive decompression, the O-ring 31 can be preferably designed and thus can have a higher oil resistance and a higher blistering resistance than the molding ring 32 , wherein the molding ring 32 instead, it may in particular have a lower permeability for the fluid than the O-ring 31 , For the form ring 32 Thus, permeation, assembly force, volume change, contact surface and avoidance of intrusion into the gap 7 between the coupling parts 1 . 2 in the foreground as interpretation criteria.

Furthermore, it can be provided in an advantageous embodiment of the invention that at least one of the peripheral seals 31 . 32 , preferably the O-ring 31 , Has a lubricious coating, such as a top material layer of the peripheral seal 31 . 32 trained sliding layer or as one on the peripheral seal 31 . 32 applied grease or oil layer, which is formed in particular of a lubricant which is contained in the fluid. As a result, each base value SW, end value E and thus also the values of the maxima M1, M2 - ie the total insertion force curve - are lowered.

9 to 11 show that the cross-section Q _{32 of} the molding ring 32 in the unpressed state "bone-like" shaped like a quadring ( 9 ) or "banana-shaped" can be curved. An elliptical training would be possible.

At the in 10 and 11 shown, "banana-shaped" execution of the molding ring 32 may be the cross-section Q _{32 of} the unpressed circumferential seal 32 are considered in the basic shape as a rectangle, which is, however, barrel-shaped arched outward. In this case, a first radius of curvature is provided for the outer, convexly curved longitudinal side and a second radius of curvature for the inner, concavely curved longitudinal side. The concave curvature of the inner longitudinal side leads in the mounted state of the peripheral seal on the second coupling part 2 and also later after plugging into the first coupling part 1 and under operating conditions advantageously to a reduction in the friction between the mold ring 32 and groove bottom 42c , because by the deformation of the thus formed molding ring 32 emerging Residual stresses reduce the pre-pressing force F _V in the central region of the inner longitudinal side. The first radius of curvature for the outer, convexly curved longitudinal side may advantageously be slightly larger than the second radius of curvature for the inner, concavely curved longitudinal side, for example approximately 0.4 to 1.6 mm, so that the convex curvature runs flatter than the concave curvature Curvature. By choosing the curvatures of the long sides of the cross section of the molding ring 32 can be set with advantage over the respective course of the long sides of a variable predetermined pressure distribution. For the transverse sides of the sealing cross-section Q ₃₂ no curvature, but a flat course is provided. The transitions from the longitudinal to the transverse sides are rounded in each case.

At the in 9 shown, "bony" version of the mold ring 32 the conditions are similar to the "bananenförimgen" execution. Again, the cross-section Q _{32 of} the unpressed circumferential seal 32 are considered in the basic shape as a rectangle, which is curved, wherein a first and a second radius of curvature are provided for the bulges. However, here the curvature is concave both for inner outer longitudinal side, as well as for the outer longitudinal side.

Due to the shape of the bone and the banana shape, pressure increases can be generated, which can ideally be expressed in an increase in the value of the maximum M2 _31/32 or in particular in a zone-wise pressure increase in the region of the gas contact surface. For example, a width B _M2 of the peak M2 _31/32 associated peaks of the curve of the insertion force FS can be changed. In 7 this width B _{M2 is} drawn in and a paragraph attributed to the specific shape of the ring geometry paragraph in the trajectory with the reference numeral A _M2 .

10 shows an embodiment in which the first groove area 41 and the second groove area 42 by an axially movable groove divider 9 are separated from each other, on which the radially circumferential ridge 8th located. The lengths L ₄₁ , L _{42 of} the two groove areas 41 . 42 are thus made variable with advantage.

In the execution according to 11 is the shaft 5 the plug-in coupling part 2 from an outer non-cutting formed tube 5a and a concentrically disposed therein on the inner wall of the tube 5a at least partially applied sleeve 5b educated. pipe 5a and sleeve 5b can - as shown - be interconnected by caulking ST. The pipe 5a forms with its deformed wall the first groove area 41 , the second groove area 42 and the intermediate radial circumferential ridge 8th out, the groove areas 41 . 42 as separate grooves 41 . 42 separates each other. Likewise, those in the second groove area 42 or the second groove 42 lying seat portion S and the compensation portion K formed by the wall contouring. Instead, the inner sleeve possesses 5b a tubular undeformed cross-section with the same diameter and a smooth wall. As a result, flow losses caused by the diameter expansions and constrictions of the outer tube 5a could occur avoided. The inner sleeve 5b can, in particular in the sense of improved thermal insulation, made of plastic, while the outer tube 5a preferably made of metal. As shown, the inner sleeve 5b at its lying in the insertion direction Z end of the outer tube 5a include and thereby directed in the direction of insertion Z groove flank 41b the groove 41 for the O-ring 31 form.

Also in the execution according to 12 is the shaft 5 the plug-in coupling part 2 formed in two parts, with a part by a non-cutting formed tube 5c is formed. Unlike the execution in 11 However, here is the non-cutting formed tube 5c inside and outside of a jacket piece 5d surrounded, which in turn outside the second groove area 42 with seat portion S and compensating portion K and between the groove portions 41 . 42 lying radially circumferential ridge 8th formed. The groove bottom 41a of the first groove area 41 gets through the pipe 5c educated. Both parts 5c . 5d can be welded or soldered together, with particular attention must be paid to a gas-tight design. The inner tube 5c is formed only in two wall portions U1, U2 and at its end U3 and is smooth-walled. As a result, flow losses due to possible turbulence in the wall area are kept small here as well. The radially outwardly widening forming region U3 at the pipe end can accommodate an annular end element 10 , serve, which is directed in the insertion direction Z groove flank 41b the groove 41 for the O-ring 31 formed.

13 and 14 , which illustrate an intermediate mounting state and the (final) mounting state of a connection system according to the invention in an eighth embodiment, illustrate that the receiving opening 6 of the first coupling part 1 via an insertion path X ₆ on the shaft 5 preassembled circumferential seals 31 . 32 for ease of insertion may have a diameter _grading D _6A , D _6B , D _6C . In particular, it is provided in the illustrated embodiment that the receiving opening 6 of the first coupling part 1 - from its insertion end for those on the shaft 5 pre-assembled perimeter obligations 31 . 32 starting - lying one behind the other a first section 6A with a first diameter D _6A , a second section 6B with a second diameter D _6B and a third section 6C having a third diameter D _6C . The diameters are constant over their sections. The first diameter D _6A is larger than the second diameter D _6B , and the second diameter D _6B is larger than the third diameter D _6C . Between the first section 6A and the second section 6B are a first conical section 6K1 and between the second section 6B and the third section 6C a second conical section 6K2 arranged.

Out 3 to 5 is in terms of facilitating the insertion of the shaft 5 on which the circumferential seals 31 . 32 are preassembled, it can be seen that in an advantageous manner the receiving opening 6 of the first coupling part 1 also a cone-shaped insertion section 6E for those on the shaft 5 preassembled circumferential seals 31 . 32 can have.

This conical shaped import section 6E in the receiving opening 6 of the first coupling part 1 may in a preferred embodiment of the insertion for the on the shaft 5 preassembled circumferential seals 31 . 32 starting one behind the other several, in particular three, sections 6F . 6G . 6H exhibit. In this case - seen in the insertion direction Z - a wall W of the coupling part 1 and the axis XX of the receiving opening 6 formed peak angle μF of the first section 6F be greater than a corresponding apex angle μG of the second section 6G and the apex angle μG of the second subsection 6G greater than the corresponding apex angle μH of the third cone section 6H ,

In connection with the remarks to 1 It had already been mentioned that the second groove area 42 may be designed geometrically such that the cross-section Q _{K of} the compensation portion K, at least over a defined axial length, in the direction Z of the axial insertion of a coupling part 2 in the receiving opening 6 of the other coupling part 1 seen in longitudinal section in the radial direction steadily and / or abruptly with respect to the cross-section Q _{S of} the seat portion S can decrease. To this the shows in 16 to 18 other possible design variants. Through these geometrical design variants, both the pre-pressing force FV ₃₂ , as well as the course of the insertion force FS (X) (see. 7 and 8th ) are optimally modified under different aspects.

16 shows that - as in the first embodiment - in the compensation section K over a defined axial length L _Ka away, one in the direction Z of the axial insertion of a coupling part 2 in the receiving opening 6 the other coupling part radially outwardly extending inclined surface 42b is trained. In addition, however, in this embodiment, it is also provided in a complementary manner that over this axial length L _Ka away, an in the direction Z of the axial insertion Z radially inwardly extending inclined surface 42d on the coupling part 1 is formed, in which the shaft 5 is inserted. This is advantageously a wedge-shaped, double-sided, compared to the first embodiment reinforced compression of the mold ring 32 achieved with increase in local compression and pre-pressing force FV ₃₂ .

In the execution according to 17 is provided that the compensation portion K and the seat portion S of the second groove portion 42 a common flat groove bottom 42c exhibit. It is provided that the cross section Q _{K of} the compensation section K in the direction Z of the axial insertion of a coupling part 2 in the receiving opening 6 of the other coupling part 1 seen in longitudinal section in the radial direction thereby jump-like with respect to the cross-section Q _{S of} the seat portion S decreases that on the coupling part 1 into which the shaft 5 is inserted, a radially inward jumping step 42e is provided.

Also 18 shows such a design in the second groove area 42 , Here, in contrast to the training according to 17 provided that the radially encircling web 8th which the first groove area 41 and the second groove area 42 separates from each other, leaving a separate first groove 41 and a separate second groove 42 are formed, also on the coupling part 1 into which the shaft 5 is inserted is located. This is the entire groove 4 in fact in the coupling part 1 into which the shaft 5 is inserted, the respective groove reasons 41a and 42c lie radially outward, and the shaft 5 is opposite to the circumferential seals 31 . 32 axially movable.

In the embodiment of the invention according to 19 is the second groove area 42 designed geometrically such that the cross section Q _{K of} the compensation section K in the direction Z of the axial insertion of the coupling part shown 2 in the receiving opening 6 of the other coupling part 1 seen in longitudinal section in the radial direction over a step 42f initially jumped relative to the cross section Q _{S of} the seat portion S reduced. This is followed by an area in which a radially inward delay fende inclined surface 42b a continuous enlargement of the cross section Q _{K of} the compensation section K in the direction Z of the axial insertion takes place.

The compensation section K is in 19 marked with a larger arrow, because the representations of the 20 ( 20a to 20c ) in each case refer to this marked section. It is apparent from these drawings that the invention is not limited to the exemplary embodiments presented above, but also encompasses all embodiments which have the same effect in the context of the invention.

In the execution according to 20a has the compensation section K over its entire length L _K a flat groove bottom 42c on, and its cross-section Q _K is - in contrast to the remarks in 20b and 20c - constant over this length L _K. To ensure the necessary compensation volume, the length L _K for this purpose is greater by an amount ΔL _K than the length L _K according to the statements in FIG 20b and 20c ,

In the execution according to 20b the compensation section K has a radially inwardly extending oblique surface over its entire length L _K 42b on, whereby the cross section Q _{K of} the compensation section K over its entire length L _K away in the insertion direction Z increases steadily. The related to the remarks in 1 and 16 mentioned length L _Ka , over which the inclined surface 42b extends, is thus identical to the entire length L _{K of} the compensation section K.

In the execution according to 20c is - similar to the first embodiment - provided that in the compensation section K via a stage 42g an additional radial compensation volume V _{R is} provided.

At the in 21 illustrated embodiment of a connection system according to the invention is in the compressed state of the already mentioned above average ring diameter DM _{31 of} the O-ring 31 - With respect to the longitudinal axis XX of the coupling part 2 - greater than the corresponding mean ring diameter DM _{32 of} the molding ring 32 , The midpoints of the cross sections Q ₃₁ , Q ₃₂ , as the mutual distance of these average ring diameter DM ₃₁ , DM _{32 are} determined, are unmarked in the figures. The maximum depth T _{41 of} the groove 41 in which is the O-ring 31 is smaller than the maximum depth T _{42 of} the groove 42 in which the molding ring 32 located. Again, it is provided that the second groove area 42 who is the groove 4 is formed for the mold ring, in a seat portion S and in a compensating portion K of smaller cross-section Q _K as the cross-section Q _{S of} the seat portion S is divided, wherein the mold ring 32 in the assembled and operating state, the seat portion S completely fills and projects into the compensation section K. In this case, it can be achieved with advantage that a contact surface, which faces the fluid as radial boundary surface GF ₃₂ (at an intermediate pressure p _Z with p ₂ <p _Z <p ₁ ), in the region of the molding ring 32 is smaller than a contact surface, which as a radial interface GF ₃₁ the fluid in the region of the O-ring 31 at the fluid pressure p ₁ faces.

What, in particular, the interpretation of 7 and 8th is concerned, it should be noted that the differentiation of the course of the insertion forces FS and the formation of their maximums in terms of their dependence on O-ring 31 and form ring 32 is not so misunderstood that the various force components occur completely individually and independently. It is that if z. B. according to the invention, first, the O-ring 31 is pressed, the existing forces then as a kind of base load the mating process of the molding ring 32 overlap. That is, if the molding ring 32 Although pressing force components primarily pass through the molding ring 32 on, but at the same time also insertion force components, especially frictional forces, through the O-ring 31 ,

The Invention is not yet defined in the claim 1 Characteristic combination limited, but can also by any other combination of certain features of all to be defined as a whole. This means, that basically virtually every single feature of the independent Claim omitted or by at least one elsewhere the application disclosed individual feature can be replaced. insofar the claims are merely as a first formulation attempt to understand for an invention.

1

first Coupling part (housing part)

2

second Coupling part (plug part)

31

Circumferential seal, O-ring

32

Circumferential seal, mold ring

4

Groove for 31 . 32

41

Groove section for 31 from 4

41a

Groove bottom of 41

41b

Groove flank of 41 (directed in Z)

42c

Groove bottom of 42

42

Groove section for 32 from 4

42a

Groove flank of 42 (opposite K)

42b

Inclined surface of 42 in 2

42c

Groove bottom of 42

42e

Stage of 42 in 1 (radially inward in Z)

42f

Stage of 42 in 2 (radially inward in Z)

42g

Stage of 42 in 2 (radially outward in Z)

5

Shank of 2

5a

outer tube of 5 ( 11 )

5b

inner sleeve of 5 in 5a ( 11 )

5c

inner tube of 5 ( 12 )

5d

outer coat of 5 around 5c

6

Receiving opening of 1

6A

Section in 6 with first diameter D _6A

6B

Section in 6 with second diameter D _6B

6C

Section in 6 with third diameter D _6C

6E

Conical import section of 6 For 2

6F

first part of 6E

6G

second subsection of 6E

6H

third section of 6E

6K1

first conical section between 6A and 6B

6K2

second conical section between 6B and 6C

7

Gap between 1 and 2

8th

Bridge between 41 and 42

9

Groove divider between 41 and 42

10

Conclusion element ( 12 )

A _M2

Sales in FS (X) in the peak of M2 _31/32

AR ₃₂

compressed radial cross-section of 32 in 42

AR _32K

compressed radial cross-section of 32 in K

AR _32S

compressed radial cross-section of 32 in S

B ₃₂

Width of 32 (unpressed), axial main dimension

B _M2

Width of the peak of M2 _31/32 in FS (X)

DM ₃₁

average diameter of 31

DM ₃₂

average diameter of 32

D _6A

first diameter of 6 , in 6A from X ₆

D _6B

second diameter of 6 , in 6B from X ₆

D _6C

third diameter of 6 , in 6C from X ₆

e

full scale the curves FS (X) (general)

E _31/31

Final value of FS (X) combination 31/31

E _31/32

Final value of FS (X) combination 31/31

E _32/32

Final value of FS (X) combination 31/31

FA ₃₁

first axial contact surface of 31

FA ₃₂

first axial contact surface of 32

FB ₃₁

second axial bearing surface of 31

FB ₃₂

second axial bearing surface of 32

FG

Filling level of 4 . 41 . 42 (generally)

FS

Insertion force (generally)

FV

jacking (generally)

FV ₃₁

Preloading force of 31

FV ₃₂

Preloading force of 32

GF ₃₁

fluid-side interface of 31 ( 21 )

GF ₃₂

fluid-side interface of 32 ( 21 )

K

Compensation section of 42

L ₃₁

length of 31 (Compressed)

L ₃₂

length of 32 (Compressed)

L ₄₁

length of 41

L ₄₂

length of 42

L _K

length from K

L _Ka

length of 42b

L _S

length from S.

M1

first Maximum of the curves FS (X) (general)

M1 _31/31

first maximum of FS (X) combination 31/31

M1 _31/32

first maximum of FS (X) combination 31/32

M1 _32/32

first maximum of FS (X) combination 32/32

M2

second Maximum of the curves FS (X) (general)

M2 _31/31

second maximum of FS (X) combination 31/31

M2 _31/32

second maximum of FS (X) combination 31/32

M2 _32/32

second maximum of FS (X) combination 32/32

p ₁

higher fluid pressure

p ₂

lower Pressure (comparative pressure, atmosphere)

p _Z

intermediate pressure

Q ₄₁

Cross section of 41

Q ₄₂

Cross section of 42

Q _K

cross-section from K

Q _S

cross-section from S.

S

Sitting section of 42

s ₃₁

Cord strength of 31 (not pressed), radial main dimension

SL ₃₁

Insertion length of 31

SL ₃₂

Insertion length of 32

SW

base value the curves FS (X) between M1 and M2 (general)

SW _31/31

Socket value of FS (X) combination 31/31

SW _31/32

Socket value of FS (X) combination 31/32

SW _32/32

Socket value of FS (X) combination 32/32

T ₄₁

maximum depth of 41

T ₄₂

maximum depth of 42

V _R

radial Compensation volume in K

W

Wall of 1 ( 15 )

X

Steckweg of 2 (current coordinate)

X ₆

Insertion path of 2 in 1 respectively. 5 in 6

X X

Longitudinal axis of 1 . 2

Z

Insertion direction of 2 in 1

ΔL _K

Difference of L _K according to 20b . 20c to 20a

μ

Coefficient of friction

uF

Angle between XX and W in 6F

ug

Angle between XX and W in 6G

.mu.H

Angle between XX and W in 6H

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - EP 1052443 B1 [0002]
• - DE 60007219 T2 [0002]

Claims (31)

Connection system for pipes, fittings or units, which are to guide a raised with respect to a comparison pressure (p ₂₎ pressure (p ₁₎ applied fluid intended, in particular for carbon dioxide-carrying systems comprising a first coupling part ( 1 ), such as a housing part, along an axis (XX) in a receiving opening ( 6 ) of the first coupling part ( 1 ) with a shaft ( 5 ) insertable second coupling part ( 2 ), like a plug part, and at least two circumferential seals ( 31 . 32 ) in the axial direction (XX) in succession in at least one circumference in one of the two coupling parts (XX) 1 . 2 ) formed groove ( 4 ) are arranged and in the assembled and operating state, a gap ( 7 ) of the receiving opening ( 6 ) and wherein a peripheral seal ( 31 ) on the side of the increased pressure (p ₁ ) in a first groove area ( 41 ) arranged O-ring ( 31 ) and the other peripheral seal ( 32 ) on the side of the comparison pressure (p ₂ ) in a second groove area ( 42 ) arranged form ring ( 32 ), characterized in that the geometry and / or the material of the peripheral seals ( 31 . 32 ) as well as the geometry of the groove ( 4 ) are matched to one another such that upon insertion of the second coupling part ( 2 ) into the receiving opening ( 6 ) of the first coupling part ( 1 ) along the axis (XX) a maximum insertion force (M2 _31/32 ) when inserting the molding ring ( 32 ) by a maximum of 20 percent of a maximum insertion force (M1 _31/32 ) when inserting the O-ring ( 31 ) deviates. Connection system according to claim 1, characterized in that the geometry and / or the material of the peripheral seals ( 31 . 32 ) as well as the geometry of the groove ( 4 ) are matched to one another such that upon insertion of the second coupling part ( 2 ) into the receiving opening ( 6 ) of the first coupling part ( 1 ) along the axis (XX) the maximum insertion force (M1 _31/32 ) when inserting the O-ring ( 31 ) not greater than the maximum insertion force (M2 _31/32 ) when inserting the molding ring ( 32 ). Connection system according to claim 1 or 2, characterized in that the geometry and / or the material of the peripheral seals ( 31 . 32 ) as well as the geometry of the groove ( 4 ) are matched to one another such that upon insertion of the second coupling part ( 2 ) into the receiving opening ( 6 ) of the first coupling part ( 1 ) along the axis (XX) the maximum insertion force (M1 _31/32 ) when inserting the O-ring ( 31 ) about the same size as the maximum insertion force (M2 _31/32 ) when inserting the molding ring ( 32 ). Connection system according to one of claims 1 to 3, characterized in that when inserting the second coupling part ( 2 ) into the receiving opening ( 6 ) of the first coupling part ( 1 ) along the axis (XX) the maximum insertion force (M2 _31/32 ) when inserting the molding ring ( 32 ) and the maximum insertion force (M1 _31/32 ) when inserting the O-ring ( 31 ) are each in the range of 40 to 100 N. Connection system according to one of claims 1 to 4, characterized in that when inserting the second coupling part ( 2 ) into the receiving opening ( 6 ) of the first coupling part ( 1 ) along the axis (XX) a plug length (SL ₃₁ ) over which the insertion force (FS ₃₁ ) is greater than half of the maximum insertion force (M1 _31/32 ), when inserting the O-ring ( 31 ) is in the range of 1 to 2 mm. Connection system according to one of claims 1 to 5, characterized in that when inserting the second coupling part ( 2 ) into the receiving opening ( 6 ) of the first coupling part ( 1 ) along the axis (XX) has a plug length (SL ₃₂ ) over which the insertion force (FS ₃₂ ) is greater than half of the maximum insertion force (M2 _31/32 ), when inserting the molding ring ( 32 ) is in the range of 3 to 5 mm. Connection system according to one of claims 1 to 6, characterized in that when inserting the second coupling part ( 2 ) into the receiving opening ( 6 ) of the first coupling part ( 1 ) along the axis (XX) has a plug length (SL ₃₂ ) over which the insertion force (FS) is greater than half of the maximum insertion force (M1, M2), when inserting the molding ring ( 32 ) is two to four times as large as the corresponding insertion length (SL ₃₁ ) when inserting the O-ring ( 31 ). Connection system according to one of claims 1 to 7, characterized in that a ratio of an axial main dimension (B ₃₂ ) to a radial main dimension (s ₃₂ ) of the molding ring ( 32 ) is greater than 1.2, preferably greater than 2.0. Connection system according to one of claims 1 to 8, characterized in that only the second groove area ( 42 ) is subdivided into a seat portion (S) and a compensating portion (K) of smaller cross-section (Q _K ) than the cross-section (Q _S ) of the seat portion (S), wherein the molding ring ( 32 ) in a pre-assembled state before insertion of the second coupling part ( 2 ) in the first coupling part ( 1 ) is located exclusively in the seat portion (S) and in the assembly and operating state, the seat portion (S) completely fills and protrudes into the compensation section (K). Connection system according to one of claims 1 to 9, characterized in that in the assembly and operating state, preferably taking into account the possible thermal expansion of the molding ring ( 32 ), as a quotient of a percentage of the compressed, radial cross-section (AR _32K ) lying in the compensation section (K) and the calculated filling degree (FG) of the cross-sectional area (AR _K ) of the compensation section (K) is less than 1. Connection system according to one of claims 1 to 10, characterized in that an axial length (L ₄₂ ) of the second groove region ( 42 ) greater than an axial length (L ₄₁ ) of the first groove region ( 41 ). Connection system according to one of claims 1 to 11, characterized in that the second groove area ( 42 ) is designed geometrically such that the cross section (Q _K ) of the compensation section (K), at least over a defined axial length, in the direction (Z) of the axial insertion of a coupling part ( 2 ) into the receiving opening ( 6 ) of the other coupling part ( 1 ) seen in longitudinal section in the radial direction steadily and / or abruptly with respect to the cross section (Q _S ) of the seat portion (S) reduced or expanded. Connection system according to one of claims 1 to 12, characterized in that in the compensation section (K), at least over a defined axial length (L _Ka ) away, a plane or ge curved, in particular convexly curved, in the direction (Z) of the axial insertion of the a coupling part ( 2 ) into the receiving opening ( 6 ) of the other coupling part radially inwardly or outwardly extending inclined surface ( 42b ) is trained. Connection system according to one of claims 1 to 13, characterized in that the first groove area ( 41 ) and the second groove area ( 42 ) by a radially circumferential web ( 8th ) are separated from each other and each have a separate first groove ( 41 ) and a separate second groove ( 42 ) form. Connection system according to claim 1 to 14, characterized in that an axial cross-sectional area (Q ₄₁ ) of the first groove area ( 41 ), in particular the first groove ( 41 ), smaller than an axial cross-sectional area (Q ₄₂ ) of the second groove area (FIG. 42 ), in particular the second groove ( 42 ) is. Connection system according to one of claims 1 to 15, characterized in that a maximum depth (T ₄₁ ) of the first groove area ( 41 ), in particular the first groove ( 41 ), smaller than a maximum depth (T ₄₂ ) of the second groove area ( 42 ), in particular the second groove ( 42 ) is. Connection system according to one of claims 1 to 16, characterized in that a ratio of a length (L ₄₁ ) to a maximum depth (T ₄₁ ) of the first groove area ( 41 ) is greater than a ratio of (L ₄₂ ) to a maximum depth (T ₄₂ ) of the second groove region ( 42 In particular, the ratio of the length (L ₄₁ ) to the maximum depth (T ₄₁ ) of the first groove region (FIG. 41 ) in the range from 1 to 5, and preferably at 3.5, and the ratio of the length (L ₄₂ ) to the maximum depth (T ₄₂ ) of the second groove region ( 42 ) in the range of 0.3 to 0.9, and preferably 0.5. Connection system according to one of claims 1 to 17, characterized in that a cord thickness (s ₃₁ ) of the O-ring ( 31 ) smaller than a radially measured line thickness (s ₃₂ ) of the molding ring ( 32 ) and / or that in the compressed state, an axial length (L ₃₁ ) of the O-ring ( 31 ) smaller than an axial length (L ₃₂ ) of the molding ring ( 32 ). Connection system according to one of claims 1 to 18, characterized in that in the compressed state relative to the axis (XX) has a mean diameter (DM ₃₁ ) of the O-ring ( 31 ) smaller than a mean diameter (DM ₃₂ ) of the molding ring ( 32 ). Connection system according to one of claims 1 to 19, characterized in that the O-ring ( 31 ) is made of EPDM and / or has a Shore A hardness in the range of 75 to 95, preferably 85. Connection system according to one of claims 1 to 20, characterized in that the molding ring ( 32 ) consists of HNBR, EPDM or FKM and / or has a Shore A hardness in the range of 75 to 85, preferably 75. Connection system according to one of claims 1 to 21, characterized in that the O-ring ( 31 ) has a higher oil resistance than the molding ring ( 32 ). Connection system according to one of claims 1 to 22, characterized in that the O-ring ( 31 ) has a higher blistering resistance and / or a higher permeability for the fluid than the molding ring ( 32 ). Connection system according to one of claims 1 to 23, characterized in that a contact surface in each case as an interface (GF ₃₁ , GF ₃₂ ), the peripheral seal ( 31 . 32 ) in the direction of the fluid, in particular in the assembly and operating state, in the region of the molding ring ( 32 ) is smaller than in the area of the O-ring ( 31 ), wherein - in the compressed or non-compressed state - the molding ring ( 32 ) preferably has a smaller mean diameter (DM ₃₂ ) than the mean diameter (DM ₃₁ ) of the O-ring ( 31 ) having. Connection system according to one of claims 1 to 24, characterized in that at least one of the peripheral seals ( 31 . 32 ), preferably the O-ring ( 31 ), has a lubricious coating, such as a top material layer of the peripheral seal ( 31 . 32 ) formed sliding layer or as one on the peripheral seal ( 31 . 32 ) applied grease or oil layer, which is formed in particular of a lubricant which is contained in the fluid. Connection system according to one of claims 1 to 25, characterized in that the cross section (Q ₃₂ ) of the molding ring ( 32 ) in the unpressed state rectangular, elliptical, banana-shaped curved or bone-like formed in the manner of a quad ring. Connection system according to one of claims 1 to 26, characterized in that the receiving opening ( 6 ) of the first coupling part ( 1 ) via a insertion path (X ₆ ) of the on the shaft ( 5 ) preassembled circumferential seals ( 31 . 32 ) has a diameter grading (D _6A , D _6B , D _6C ) for ease of insertion. Connection system according to one of claims 1 to 27, characterized in that the receiving opening ( 6 ) of the first coupling part ( 1 ) - from its insertion end for those on the shaft ( 5 ) preassembled circumferential seals ( 31 . 32 ) starting - lying one behind the other a first section ( 6A ) with a first diameter (D _6A ), a second portion ( 6B ) having a second diameter (D _6B ) and a third portion ( 6C ) having a third diameter (D _6C ), wherein the first diameter (D _6A ) is greater than the second diameter (D _6B ) and the second diameter (D _6B ) is greater than the third diameter (D _6C ). Connection system according to claim 28, characterized in that between the first section ( 6A ) and the second section ( 6B ) a first conical section ( 6K1 ) and between the second section ( 6B ) and the third section ( 6C ) a second conical section ( 6K2 ) is arranged. Connection system according to one of claims 1 to 29, characterized in that the receiving opening ( 6 ) of the first coupling part ( 1 ) has a cone-shaped insertion section ( 6E ) for those on the shaft ( 5 ) preassembled circumferential seals ( 31 . 32 ) having. Connection system according to claim 30, characterized in that the cone-shaped insertion section ( 6E ) in the receiving opening ( 6 ) of the first coupling part ( 1 ) from the insertion end for the on the shaft ( 5 ) preassembled circumferential seals ( 31 . 32 ) starting in succession three subsections ( 6F . 6G . 6H ), wherein - seen in the insertion direction (Z) - one of the wall (W) of the coupling part ( 1 ) and the axis (XX) of the receiving opening ( 6 ) formed peak angle (μF) of the first section ( 6F ) is greater than a corresponding peak angle (μG) of the second subsection ( 6G ) and the apex angle (μG) of the second subsection ( 6G ) is greater than the corresponding apex angle (μH) of the third cone section ( 6H ).