CH634903A5 - Socket connection of pipes and pipe elements. - Google Patents

Description

634 903

PATENT CLAIMS

1. Push-in socket connection of pipes and pipe elements with a smooth plug-in end and a socket end receiving this with radial play, which has an approximately radial end shoulder in its interior and an annular bulge at an axial distance from it, between which the foot section of a sealing and thrust securing ring can be inserted , which has a sealing section on the side of the annular bead facing away from the foot section and to which a plurality of holding elements made of metal distributed in the circumferential direction are fastened, which have at least two tooth-like inner edges for engaging on the circumference of the smooth insertion end and are tiltably supported on the annular bead, the radial outward-facing circumferential surface of each holding element diverges from the envelope portion touching all the inner edges toward the sealing section, characterized in that the radially outward-facing peripheral surface is designed as a sliding surface (8b, 53, 69) and each in the Sealing material embedded retaining element (4) with this sliding surface on the annular bead (19, 43, 63) is both guided axially displaceably and is supported in any axial position in a freely tiltable manner.

2. Push-in socket connection according to claim 1, in which an approach engaging with axial play in the annular groove in the radial direction outwardly on the holding element is provided, characterized in that on the surface (8a) of the annular bead (19) facing the annular groove (30 ) projecting approach (6) of each holding element (4) a soft rubber pad (8c) is provided.

3. push-in socket connection according to claim 2, characterized in that the end shoulder (20) facing surface (7) of the in the annular groove (30) protruding approach (6) of each holding element (4) in radially extending planes towards the end shoulder (20) convex is curved.

4. push-in socket connection according to claim 1, characterized in that each holding element (50,68) is limited in its axial displaceability solely by the end shoulder (41,59).

5. push-in socket connection according to claim 4, characterized in that the end shoulder (41,59) facing the end of the sliding surface of each holding element has a cooperating with the end shoulder deflection curve (52, 72).

6. push-in joint according to Claim 4 or 5, in which the annular bead is delimited on its side facing away from the end shoulder by an inclined surface which forms an acute angle with the joint axis, characterized in that at least one of the interacting sliding and guiding surfaces (53, 44 or 62, 69) is convexly or convexly curved toward the other surface.

7. push-in joint according to one of claims 1 to 6, characterized in that the divergence angle (10) depending on the axial length of the glide path (9) is selected so that the radial distance (23) between the positions in one to the axis the parallel position of the insertion end tilted envelope surface (14) at the two ends of the sliding path is equal to or greater than half the maximum permissible diameter difference of the insertion end (15).

8. push-in socket connection according to one of claims 1 to 7, wherein each holding element has at least three tooth-like inner edges, characterized in that the sleeve line (14) touching all inner edges simultaneously is a straight line.

The invention relates to a push-in socket connection of pipes and pipe elements, in particular made of metal.

Such push-in socket connections of pipes made of metal with a smooth insertion end and one with a radial

Game-receiving socket ends are known (cf. DE-PS 2 226 151). In this known push-in socket connection, the tooth-like inner edges of each holding element are designed such that they have different axial and radial sections from the tilting axis of the holding element depending on the permissible diameter tolerance of the insertion end. Each holding element is essentially only movable about its tilt axis. The arrangement is such that only one tooth-like inner edge or a group of tooth-like inner edges is in engagement with the circumference of the insertion end in each tilted position, wherein essentially the same and optimal engagement states with regard to the transmission of the forces occur in each tilted position. The known push-in joint connection thus results in reliable engagement states over a certain tolerance range with regard to the diameter of the push-in end or the inside diameter of the push-in end, which ensure that pushing and pulling forces are reliably absorbed via the push-in joint connection without the sealing effect being impaired. This push-in joint has therefore proven itself very well in practice.

However, it has proven problematic, at least under certain circumstances, that only a limited part of the tooth-like inner edges available engages on the circumference of the insertion end in each angular position of the holding elements. This results in force concentrations along linear engagement areas. The result can be undesirable high notch effects, which in some cases can also lead to damage or destruction of the insertion end, especially when the push-in joint is exposed to alternating forces.

It is an object of the invention to remedy this situation and to further develop the push-in socket connection in such a way that, while ensuring the thrust safety effect, the forces required for this are distributed over areas of the insertion end that are more extensive in area, while at the same time an even greater tolerance range with one and the same sealing and thrust locking ring can be safely and reliably controlled with regard to the diameter deviations of the parts.

This object is solved by the features of claim 1.

Due to this design, each holding element can not only tilt freely and independently of the other holding elements, but can also move freely in the axial direction. First of all, this means that, regardless of their position and regardless of the existing diameter tolerances of the pipe parts to be connected, each holding element assumes a position in which practically all tooth-like inner edges of the holding element act simultaneously and essentially under the same load on the circumference of the insertion end. The same engagement conditions and a uniform distribution of the radial clamping forces over larger surface areas of the circumference of the insertion end are thus always and independently obtained from irregularities of the surfaces at the insertion end. In no case can undesirably high notch effects occur. Nevertheless, larger diameter tolerance ranges can be reliably controlled with one and the same sealing and thrust retaining ring. Due to the simultaneous axial sealing and thrust retaining ring, the retaining element has the effect of a wedge that is displaced in the axial direction under the forces that arise until, while simultaneously tilting to adapt to the shape and the nature of the surface of the insertion end, the greatest possible clamping force on the Transmits the scope of the insertion end.

Such wedge effects are known per se for securing against thrust (cf. DE-PS 2 034 325). However, this is a different situation, because thrust protection and seal in

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this known case are separated from one another and therefore it has also proven advantageous in some cases

two separate elements installed in each pipe connection if the outward sliding surface of each holding element must be. compared to the corresponding outer envelope surface of the elasto-

In contrast, the new plug-in joint ring is set back a little radially inwards,

binding around such a training, in which a seal and 5 is at least exposed, i.e. not of elastomeric material

Push lock ring is used as a structural unit in which the is covered. This facilitates insertion and the exact holding elements are firmly installed in this unit. Below this, alignment of the holding element while reducing the

it is understood that they are captive forces with the sealing ring. In cases where the pipe connection

glued, vulcanized or otherwise connected. good electrical contacts are to be ensured

However, this does not mean that the holding elements with the 10 thereby have better metallic contact between holding elements.

Sealing and thrust retaining ring form a rigid unit. ment and sleeve ensured. In addition, the

Rather, the ring as a whole is deformable, in order to be inserted into the frictional forces during the relative movements, which is still

to lighten the sleeve. In addition, the holding elements are supported when at least one of the cooperating parts can be tilted relative to the elastomeric parts of the ring and can also be axially displaced with a wear-resistant and electrically insulating surface. The elastomeric part is covered with a 15 layer. This is desirable in some cases, e.g.

Foot section in a groove against axial displacement when an electrically conductive connection is made via the pipe connection

anchored. connection between the interconnected pipe parts

If the holding elements are to be casually prevented from pointing radially outwards.

Have approach, which engages in the inner groove of the sleeve, for the new training needs the usual shape of the sleeve

This is a smaller dimension in the end of the groove than the inner groove, regardless of whether the direction of the sleeve axis is open. Thus, the axial sliding sealing portion of the sealing ring is teardrop-shaped,

movement of the holding element in both axial directions, for example in the case of the seal known under the name "Tyton"

limits a predetermined amount. The arrangement is preferred, or else it is designed as a double lip. However, it can be done without a radial approach, so that the axial can also be particularly useful if that of the end shoulder

Mobility of the holding element only in an axial direction, 25 opposite side of the annular bead form an oblique contact surface.

and is limited by the end shoulder of the sleeve. det with the sleeve axis an acute angle, preferably

When inserting the smooth pipe end, the seal is enclosed between 20 ° and 30 °.

ring deformed in its sealing portion. At the same time, the invention is

the holding elements with the envelope surface of the toothed inner openings explained in more detail in several exemplary embodiments, aligned with the axis of the smooth pipe end. You can show 30 it:

When inserting the smooth pipe end axially from FIG. 1 in a cutout and in a longitudinal section, a typical sleeve

Move the end shoulder away to create the clear connection without a sealing and thrust retaining ring,

2 the cross-sectional shape of a generally known

enlarge until the smooth pipe end under sliding friction after the sealing ring, which is called "Tyton seal"

can be pushed inside. Here the tooth-like 35 is in the hand

3 on a larger scale than FIGS. 1 and 2, an inner edge of the holding elements is already free on the insertion end. As soon as the desired installation condition of the new push-in joint, FIG. 3

is reached, the reshaping force in the elastomer provides a cross section through the sealing

Part of the sealing ring for a certain preload with which and thrust retaining ring represents,

the holding elements in the direction of the end shoulder of the sleeve 40 Fig. 4 in a similar representation, the push-in socket connection are biased. This preload holds the holding elements and the function of the holding elements which are in the ring according to FIG. 3

in contact with both the sleeve and the insert. To simplify, the elastomeric end is in FIG. 4. Accordingly, the prestressing is not shown in part of the ring,

light clamping force on the insertion end. As soon as FIG. 5, in a representation similar to FIG. 3, a modified occurring force increases by increasing the pressure in the interior of the exemplary embodiment and the pipeline, the axial displacement also increases. FIG. 6, in a representation similar to FIG. force on the holding elements, which wedge-shaped in the gap deltes embodiment of the new push-in joint, between the contact surface of the sleeve and the circumferential surface of the push-in joint shown in Fig. 1 serves to insert the plug-in end in the axial direction on the end shoulder pipe part A with the pipe part B to connect. The pipe parts A ben, so that the radial clamping force on the insertion 50 and B have at one end a push-in sleeve 17 and at the other end to enlarge accordingly. The transfer of forces end up with a smooth male end. Fig. 1 shows the installation-over the inner edge of the holding elements is optimal, since the two parts are at the same time. In this state surrounds the Steckmuffe term the holding elements can give away as desired and 17 the smooth tube end with radial play, the size of which varies reliably in the axial direction on the course of the peripheral surface of the insertion end of this game. Adjust near the exit. 5S end of the sleeve, an annular groove 30 is provided between

If a holding element is limited with its front end against that of an end shoulder and an annular bead 19. Beyond

Butting the end shoulder, a sealing chamber 18 formed on the front end of the retaining ring 19 follows a deflection curve formed on a larger element to ensure that this end is wide. This serves to receive the sealing section of the retaining element deflected in the radial direction inward sealing and thrust retaining ring. To the sealing chamber

and is pressed against the circumference of the insertion end. Here 6t mer 18 is connected to a transition chamber 18a, which is in one the holding element with the sleeve in two mutual axial gap 18b between the ring base of the sleeve and the axial distance in contact lines, which is the end face of the insertion end. The arrangement is

Function of the thrust protection in no way impaired. Made in such a way that the two pipe elements A and B

The interacting surfaces from the holding state make relative swiveling movements or curse

ment and sleeve are preferably designed so that only 65 misalignment of their axes can occur without the parts resulting in low frictional forces. For this purpose it is not necessary to touch one another.

at least one of these two surfaces in the direction of the other. In the case of the sleeve shape shown in FIG. 1, it is preferred and of convex or spherical design. Usually used a sealing ring, the outline shape

634 903

is shown in Fig. 2. The sealing ring 1 has a spherical sealing section 2a made of softer rubber and an adjoining foot section 2b made of relatively hard rubber, which has an annular groove 2c on its outside for receiving the annular bead 19. 5

3 and 4, a plurality of holding elements 4 arranged in the circumferential direction at mutually spaced intervals are firmly embedded, for. B. glued or vulcanized. The holding elements 4 have a limited partial ring-shaped circumferential expansion. Each holding element 4 10 has on its radail inner side a plurality of toothed engagement edges 5a, 5b, 5c and 5d, which in the example shown lie with their cutting edges on a common truncated cone-shaped envelope surface 14. Radially on the outside, each holding element 4 is delimited by a circumferential surface, which likewise lies on a truncated cone-shaped envelope surface 8b. The envelope surface 14 and the circumferential surface 8b diverge in the axial direction away from the end shoulder 20. The divergence angle is denoted by 10 and is expediently in the range between approximately 25 ° and approximately 45 °. It is preferably about 30 °. 20th

It can be seen that the holding elements 4 are essentially embedded in the foot section 2b of the sealing ring, that is to say in the hard rubber part. The tooth-like inner edges are exposed to the inside. In the example of FIGS. 3 and 4, in the area of the tapering end, each holding element 4 has a projection 6 projecting radially outwards, which engages in the annular groove 30 between the end shoulder 20 and the annular bead 19 in the installed state, as is shown in FIGS. 3 and 4 emerges. The axial extension of the extension 6 is small compared to the axial width of the annular groove 30. On the boundary side 8a of the extension 6 facing the annular bead 19, the extension can have a soft rubber pad 8c which, when deformed, provides a pretension, which the end element 4 strives for to press down in Fig. 3.

It can be seen that, due to the axial displacement space designated by 9 in FIG. 3 and the abutment of the outer surface 8b of the holding element 4 on the annular bead 19 of the holding element, they move axially to a limited extent in the direction of the double arrow 11 in FIG. 3 and at the same time freely around can pivot about the axis 13 of the circularly curved annular bead 19 according to the double arrow 12.

In order to enable the pivoting also in the limit position shown in FIG. 3, the end face of the holding element facing the end shoulder 20 is convex or convex,

as indicated at 7 in Fig. 3.

FIG. 4 shows the arrangement in the installed state, specifically for different diameters of the insertion end 15. The sealing and thrust retaining ring according to FIG. 3 assumes the position indicated in FIG. 3 after insertion into the sleeve shown in broken lines according to FIG. 3. When the smooth pipe 50 of the 15 is pushed in in the direction of the arrow 32, the peripheral surface 16 of the pipe end comes into contact with the toothed inner edges of the holding element 4 and the elastomeric material. The holding elements 4 are axially displaced in the direction of insertion and simultaneously pivoted until the inner edges lie uniformly against the circumference of the insertion end. Movement of the sealing ring as a whole is prevented by the engagement of the foot section 2b (see FIG. 2) in the annular groove 30. With 21, the end position of the holding element with a very small diameter of the insertion end 15 is shown in solid lines, while with 22 60 the position of the holding element with a large diameter of the insertion end 15 is shown in dashed lines. With 23 the tolerance range with respect to the diameter is indicated, which can be reliably accommodated with one and the same sealing and thrust securing ring. 55

The arrangement in the installed state is shown in FIG. 4, specifically for different diameters of the insertion end 15. The sealing and thrust securing ring according to FIG. 3 decreases

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Insert into the sleeve shown in dashed lines in FIG. 3 the position indicated in FIG. 3. When inserting the smooth pipe end 15 in the direction of arrow 32, the peripheral surface 16 of the pipe end comes into contact with the toothed inner edges of the holding element 4 and the elastomeric material. The holding elements 4 are axially displaced in the direction of insertion and at the same time pivoted until the inner edges lie uniformly on the circumference of the insertion end. Movement of the sealing ring as a whole is prevented by the engagement of the foot section 2b (see FIG. 2) in the annular groove 30. With 21 the end position of the holding element with a very small diameter of the insertion end 15 is shown in solid lines, while with 22 the position of the holding element with a large diameter of the insertion end 15 is shown in dashed lines. With 23 the tolerance range with respect to the diameter is indicated, which can be reliably accommodated with one and the same sealing and thrust securing ring.

If, after installation, hydraulic or other pressure is exerted on the soft rubber section 2 by the internal pressure in the pipeline, which is indicated by the arrow 31 (FIG. 4), each becomes over the soft rubber of the sealing ring (Fig. 2, number 2a) Holding element 4 axially displaced in the direction of the shoulder 20 with high force and thus pressed in in a wedge shape between the peripheral surface 16 of the insertion end 15 and the annular bead 19. These forces act via the inner edges of the holding elements 4 as radial clamping forces on the circumference of the insertion end and reliably secure the insertion end against any axial displacement force. The forces are distributed over larger peripheral areas.

In the exemplary embodiment according to FIG. 5, it is assumed that the sleeve 40 is essentially similar to the sleeve according to FIG. 1. The end shoulder is designated 41, the annular groove 42, and the annular bead 43. It is further assumed that the elastomeric sealing ring 45 is constructed similarly to that in FIG. 2. The soft rubber section is designated 46 and the foot section made of harder rubber 49. A plurality of holding elements 50 are fixedly embedded in the elastomeric ring, each of which has four inwardly facing, toothed inner edges 51 and an essentially frustoconical outer surface 53. The holding elements 50 have no shoulder engaging in the groove 42. Instead, the narrower axial end 52 is provided with a deflection curve which, when it hits the end shoulder 41, ensures that the narrow end of the holding element is pressed radially inward against the circumference of the insertion end. It can be seen that the outer surface 53 of the holding element can be offset radially inwards relative to the outer peripheral surface 48 of the ring. This area of the holding element can also be free of elastomer. The surface 53 can therefore be exposed via a kind of window 47 on the outside of the sealing ring. What is important is only a direct contact of the surface 53 with the bead 43 of the sleeve without pinching the elastomer.

In this embodiment, the displaceability of the holding element 50 in the axial direction is limited only in one direction, namely in the direction of the end shoulder 41, specifically by this end shoulder.

The side of the annular bead 43 of the sleeve facing away from the end shoulder 41 is expediently limited, as indicated by dashed lines at 44, by an inclined surface which includes an acute angle, preferably between 20 ° and 30 °, with the sleeve axis. If, as shown in FIG. 5, the outer sliding surface 53 of the holding element 50 is essentially flat, the inclined surface 44 is preferably spherical, as indicated.

A somewhat modified embodiment which corresponds to the exemplary embodiment according to FIG. 5 is shown in FIG. 6. The annular groove 64 of the sleeve 60 has a semicircular contour and merges into the oblique end shoulder 59. The the

Groove 64 delimiting bead 63 can be rounded or, as shown, cylindrical and is delimited on the side facing away from groove 74 by an inclined surface 62 which forms an acute angle 58 with the axis of the sleeve. The double-lip-shaped soft rubber section 67 of the directional and thrust securing ring 65 comes to rest in the sealing space 61 of the sleeve. At the lower end, this has an annular bead of essentially circular outline, which is denoted by 66 and engages in the annular groove 64 in order to anchor the sealing ring in the sleeve. A plurality of circumferentially distributed holding elements 68 are vulcanized between the bead section 66 and the soft rubber section 67, three of which, as shown in solid lines, or four as shown in dashed lines at 73,

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has tooth-shaped inner edges 70. The outer sliding surface 69 or 69a is convexly curved to the outside and is freely accessible at 71, uncovered by the elastomer composition, possibly slightly 5 radially inwardly offset from the outer circumferential surface of the ring (which is strongly exaggerated in FIGS. 5 and 6) ). In this exemplary embodiment, the holding elements 68 are practically freely displaceable in both axial directions and can pivot freely in any axial position, as is also the case with the exemplary embodiment according to FIG. 5. At 80, the possible tolerance range in the diameter of the insertion end is shown in FIG. 6, which can be accommodated by one and the same sealing and thrust securing ring.

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