DE4121406C1 - Pipeline compensator for axial, angular, and lateral motion - has third bellows inserted in intermediate pipe, supported against lateral and angular motion - Google Patents

Abstract

The compensator absorbs lateral, angular, and axial movement between two pipeline ends (1, 2) and is tightly joined by tubular connecting ends. It has two annularly corrugated bellows (3, 4) between which is fitted an intermediate pipe (5, 6). A third bellows (7) is inserted into the intermediate pipe and is supported by an inner or outer pipe parallel to it, with an inner or outer slightly less or more than those of the third bellows. Arms (10-13) protrude from parts of the intermediate pipe and fromt he connecting ends. ADVANTAGE - Reduced risk of destruction for the first two bellows.

Description

The invention relates to a pipe compensator for Acquisition of lateral, angular and axial movement quantities between two pipe ends, the one with the pipe pipe ends tightly ver over tubular connection ends tied compensator in the area next to the An concluding a first and a second ring-corrugated Bellows and an intermediate tube connecting the bellows points.

Such known pipe expansion joints serve before especially the acquisition of axial and lateral movement quantities between two opposite pipelines end, although in some cases even minor Angular portions are added.

So far the known compensators pure lateral compensators are, that is, mutual lateral displacement movements compensate for pipe ends, with the axes the opposite pipe ends the first and second bellows remain parallel compared to the total installation length of the compensator relatively short. The mutual lateral offset the opposite pipe ends largely taken over the intermediate tube, the  the two bellows mentioned essentially angular movements have to record or be angled.

But now such a compensator is also included an axial amount of movement applied, for example wise due to thermal expansion by changing the length of the intermediate can be caused and also in that the mutual distance between the pipe ends changes, this requires additional axial movement size much longer bellows, the tendency to lateral chem pushing away or buckling, which increases especially with small nominal diameters of the line has an adverse effect by deforming the bellows inadmissibly and thus suffer irreversible damage. This causes the bellows to be only proportionate moderately small number of movement cycles can be destroyed. A normal internal pressure load on the line plays here and thus the bellows play a significant role in the end kink the bellows and thus their local elongation significantly enlarged.

The object of the invention is a pipeline compensation further educate gate of the type mentioned or to add that a risk of destruction for the first and second bellows due to axial movement quantities at least on a practically no longer weight falling dimension is switched off.

This object is achieved in that in a third ring-corrugated bellows is inserted into the intermediate tube sets, and that this third bellows against angular and Lateral movements is supported.

This measure according to the invention is a division for the recording of angular movement variables on the one hand  and the axial amount of movement on the other hand achieved that now knows the angular motion quantities Tested by the first and second bellows be, while the axial amount of movement by the third bellows is intercepted. So the first and second bellows relieved of axial movement quantities and it is on the other hand the third bellows of angular Movement sizes relieved. The axial amount of movement is So caught by the third bellows, so that for the first and second bellows mostly only one angular movement left over, these two last-mentioned balls ge within the permissible framework provided for them speaks. The first and second bellows can be short be trained.

Because the third bellows against angular and lateral is supported, it can be relatively soft be trained so that he without considerable resistance compensate for the axial movement quantities that occur can.

It has proven to be expedient that the third bellows abge through an inner or outer tube parallel to it is supported, the outer or inner diameter is small gig smaller or larger than the inside or outside knife of the third bellows is that the inside or outside pipe inside or outside the compensator and of the third bellows extends at least over a length, that of the length of the third bellows plus one with the axial movement size of the third bellows match corresponds to the length, and that the inner or outer tube with one of its ends on the part assigned to it the intermediate pipe is attached. By this measure is the third bellows with the help of the inner or outer tube  supported against lateral movement, the interior or outer tube in the axial direction over the third bellows with its unattached end again in the part of the intermediate tube extends there, so that practically the two parts of the intermediate tube that with are connected to the third bellows by the inner or Outer tube with regard to lateral and angular movement size are supported against each other. Mutual Axialbe movements of the two associated with the third bellows However, parts of the intermediate tube are through the inside or outer tube not hindered.

In a further development of the subject matter of the invention, it can be advantageous that in addition first and second bellows through them each overlapping outside, from the connector ends of the compensator and the associated parts of the Intermediate tube outgoing arms against axial movement ge are secured that the arms are diametrically opposed to each other overlying outer sides of the compensator axially parallel are arranged, and that each of the connections the outgoing arms articulated with those of the intermediate ones tube parts outgoing arms are connected, each because both arm pairs have a common one, for the compensator axis se have a radial axis of rotation. This design closes both plane movements with two diametrically opposite each other opposite pairs of arms, as well as gimbal movement opposite each other with pairs offset by 90 ° the pairs of arms.

Articulated arm arrangements of this type are known per se. they in the present case, however, lead to the fact that first and second bellows completely of axial loading Movement variables are also exempted insofar as these  possibly still by the reaction force of the axial ver formed third bellows could be triggered. In order to first and second bellows can be relatively short and be made stiff to suit one withstand considerable angular stress.

In this sense, it is then also expedient that the first and second bellows stiff in the axial direction are formed over the third bellows, whereby this Stiffness refers to the respective axial movement capacity of the individual bellows wave.

Further features and details of the invention emerge from the following description of an execution form based on the drawing. Show in the drawing

Figure 1 is a pipe compensator in the axial half section.

Fig. 2 shows a detail of Fig. 1 rotated by 90 ° and

Fig. 3 shows the axial compensator of FIG. 1 in deflected ter and axially length-shifted position.

As can be seen from FIGS . 1 to 3, a pipe expansion joint has connection ends 1 , 2 which can be connected in a manner not shown because known ends with pipe ends, for example by mutual welding.

At the terminal ends 1, 2, 4 each include a Annularly corrugated bellows 3, to, wherein the bellows 3, 4 in a manner usually welded to the terminal ends 1, 2 can be.

Between the bellows 3 , 4 , the parts 5 , 6 of an inter mediate tube are arranged, which accommodate a third bellows 7 between them, and here, too, the mutual connection can again be made in a manner known per se by welding.

Inside the parts 5 , 6 of the intermediate tube and the third bellows 7 , an inner tube 8 is arranged, which is welded to the intermediate tube part 5 at 9 . Within the intermediate tube part 6 , on the other hand, the inner tube 8 is exposed, so that it allows axial movements of the intermediate tube parts 5 , 6 against one another without, on the other hand, allowing their mutual lateral or angular movement to a significant degree. For this purpose, the inner tube 8 is provided with an outer diameter that is slightly smaller than the inner diameter of the third bellows 7 and the intermediate tube part 6 . The length of the inner tube 8 is sized so that it remains over the entire range of axial motion to be expected Tenden size with its free end within the intermediate tube portion 6 and can find its lateral abutment or support there.

As can be seen from FIGS. 1 to 3, parallel to the first and second bellows 3 and 4, the articulated arms 10, 11, 12, 13 are arranged. The articulated arms 10 , 13 are firmly connected at one end to the connecting ends 1 and 2, for example by welding, while the articulated arms 11 , 12 are welded at their one end to the intermediate pipe pieces 5 and 6, respectively. With the respective other end, the articulated arms are pivotally connected to one another by means of a bolt 14 , 15 , the bolt axis being arranged radially to the pipe compensator. This known articulated arm arrangement serves to allow for the ring-corrugated bellows 3 , 4 only a pure angular or angular movement about the axis of the bolt 14 or 15 , but without an axial movement share on the bellows 3 , 4 can go.

Compared to the illustration in FIG. 1, FIG. 3 shows a deflected pipe compensator. Here is ersicht Lich that the bellows 3 , 4 are kinked or moved angularly, while the bellows 7 had to take on an axial amount of movement in that the axial spacing of the connecting ends 1 , 2 did not change each other, but on the other hand by the apparent lateral offset, the connecting path between the connection ends 1 , 2 has become larger. This mutual lateral movement of the connection ends 1 , 2 , however, does not impose an angular movement on the third bellows 7 because, on the other hand, it is supported by the inner tube 8 , which with such a lateral movement comes into contact with the intermediate tube part 6 with its free end.

The design described with reference to FIGS . 1 to 3 allows the ring-corrugated bellows 3 , 4 to be designed to be relatively short and stiff, since they only absorb angular movement variables. In contrast, the third bellows 7 can be made relatively long and soft, so that it is able to absorb larger axial movement components and to relieve the bellows 3 and 4 .

In the illustrated embodiment, the usual design of such a pipe expansion joint made of metal is intended. Of course, however, there is also the possibility of producing such in the same way from plastic parts, depending on the conditions of use. It is also entirely possible to omit the articulated connection represented by the arms 10 to 13 , if the force and movement conditions occurring permit this.

Claims (4)

1. Pipe compensator for absorbing lateral, angular and axial movement variables between two pipe ends, the compensator which is tightly connected to the pipe ends via tubular connecting ends each having a first and a second ring-corrugated bellows in the area next to the connecting ends and an intermediate pipe connecting the bellows, characterized in that that a third ring-corrugated bellows ( 7 ) is inserted in the intermediate tube ( 5, 6 ), and that this third bellows is supported against angular and lateral movements. 2. Pipe expansion joint according to claim 1, characterized in
that the third bellows ( 7 ) is supported by an inner ( 7 ) or outer tube parallel to it, the outer or inner diameter of which is slightly smaller or larger than the inner or outer diameter of the third bellows,
that the inner or outer tube extends inside or outside the compensator and the third bellows at least over a length which corresponds to the length of the third bellows plus a length which corresponds to the axial amount of movement of the third bellows and
that the inner or outer tube is attached with one of its ends to the associated part ( 5 ) of the intermediate tube ( 5, 6 ). 3. Pipe compensator according to claim 1, characterized in
that the first ( 3 ) and second bellows ( 4 ) through them each overlapping, from the connecting ends ( 1 , 2 ) of the compensator and the associated parts ( 5 , 6 ) of the intermediate tube outgoing arms ( 10 to 13 ) are secured against axial movement ,
that the arms are arranged axially parallel to one another on the opposite outer sides of the compensator, and that the respective outgoing arms ( 10 , 13 ) are connected in an articulated manner to the arms ( 11 , 12 ) extending from the intermediate tube parts ( 5 , 6 ) are, wherein both pairs of arms have a common, radial axis to the compensator axis of rotation (bolts 14, 15 ). 4. Pipe expansion joint according to claim 1, characterized in that the first and second bellows ( 3 , 4 ) in the axial direction are rigid with respect to the third bellows ( 7 ).