SK278379B6 - Device for holding of pipe, in particular the pipes in a power station - Google Patents

Abstract

Device for holding of pipe (1), in particular the pipe (1) in the power station, is created based on the hinge support (2) which is fixed to the anchor (4) with the use of one its end, so that its rotating to be possible, this anchor is connected to the building skeleton (3) and the second end of it is connected to the clip (5) holding the pipe (1). The clip (5) is created with the use of the coupler (6) with the bed (13) placed under the pipe (1) and equipped with the hinge gripper (7) and with one loop (8) at least surrounding the pipe (1). The pipe (1) is in the bed (13) and it is placed on two gate surfaces, while these surfaces are dislocated on the fractional parts related to the arc (14) of the outer tangential surface (15) of the pipe (1), sealing on the bed (13) and the curvature radius closed to the sealing surfaces is greater than the radius closed to the pipe (1).

Description

Technical field

The invention relates to a pipe holding device, in particular a pipe pipe in a power plant, with a hinged support which is rotatably connected at one end to an anchor connected to a building frame and at its other end rotatably connected to a tube retaining clip. below the pipe and equipped with an articulated coupling carrier and at least one loop surrounding the pipe.

BACKGROUND OF THE INVENTION

Such a holding device is known in various embodiments with one or more articulated supports for each clip, see, for example, Power magazine of September 1976, pages 100 to 104, in particular the drawing on p. 100. The printed work is entitled Shock restraint for nuclear fluid lines in fast-developing area of piping support, author: Harold Erikson. The so-called yoke clamps are also included with said holding devices.

By means of these holding devices, not only tensile forces but also compressive forces are transferred from the retained pipe to the building by means of articulated supports. When the pipe clamp is not sufficiently matched to the pipe wall, the transverse forces arising from the angular deflection of the articulated support relative to the pipe axis and the resulting frictional force between the pipe clamp and the pipe wall shall be absorbed. In this case, the tensioning of the pipe clamp in the tension by the articulated support is not considered to be a critical stress, since the articulated support pulls the pipe clamp to its stable middle position. Rather, the force of the articulated support exerting pressure on the pipe clip is of note; with respect to these compressive forces, the securing device with the pipe clamp must be secured against rotation and displacement and must be demonstrable by frictionally connecting the pipe clamp under a defined compressive force at defined deviations of the articulated support axis from the normal wall of the pipe. Until now, this friction connection has been achieved by a relatively high preload of the clip on the tube. This causes additional local stress on the pipe wall. The tube is pressed against the sharp edges of the bed, thereby damaging it.

SUMMARY OF THE INVENTION It is an object of the invention to provide a pipe tube holding device which has a high degree of safety against undesirable rotational or sliding movements and which does not additionally stress the pipe wall by bending the pipe clip.

SUMMARY OF THE INVENTION

A tube holding device, in particular a pipe tube in a power plant, with a hinged support which is pivotally connected to its anchor connected to the building frame at one end and pivotally connected to the pipe retaining clip by its other end. under the pipe and equipped with an articulated coupling carrier and at least one loop encircling the pipe, according to the invention, which is characterized in that the pipe is supported in the bearing on two bearing surfaces, these bearing surfaces extending only on a fraction of the arc section of the outer circumferential surface and the radius of curvature of the bearing surfaces is greater than the radius of the pipe.

As a result, the force action of the clamping forces is located on narrowly defined abutment surfaces, but which have no sharp edges which could damage the pipe.

Further advantageous embodiments are set forth in claims 1 to 11.

For example, the clip loop has a thickness D _s = k. Wr and width B _s = m / n. Wr, where Wr is the wall thickness of the tube, k as well as m are dimensionless quantities, as determined by 10 experiments, where <1, m> lan is the number of loop loops.

For example, the wall thickness of the clip loop is less by a factor of k (k < 1) than the wall thickness of the tube to be held, preferably significantly less, with a value of a factor of 15 of about 0.1 to 0.5. In this case, the larger factor k is suitable for pipes with a smaller wall thickness and the smaller factor k is suitable for pipes with a greater wall thickness. This reduced wall thickness of the loop loop provides the good bending necessary to properly adapt the loop loop to the tube wall within the wrapping range so that deformation of the upper part of the tube is practically avoided. When the loop loop extends into the threaded ends, the clamping force transmitted by these threaded ends is appropriately small. The small thickness of the loop loop further has the advantage that the temperature differences between the tube wall and the loop loop, and therefore the voltage variations from the different thermal elongations, remain small.

Preferably, the bearing surfaces are mirror-symmetrical to each other on both sides of the plane of symmetry, this plane of symmetry extending through the axis of the pipe with the center of the clip coupler. The angle of expansion 2 γ, which has a vertex in the pipe axis and whose arms are the axes of both bearing surfaces, lies within a range of 35 ° <2 γ <100 °, the arcuate section of the bed being slightly larger. In this way, two relatively large force vectors arise when the clamping force and the articulation force are distributed, both force vectors being statically definite and directed from the bearing surfaces 40 to the pipe axis so that they pass through the center of the pipe.

This results in high adhesion forces and a suitable force application area for the elastic deformation of the lower and upper half of the pipe.

A preferred embodiment further comprises that each of the two bearing surfaces is located in the outer region of the duct bearing seat, wherein the opening angle (2 y) of the support is at least 60 °.

For example, each bearing surface extends over a portion of the arcuate section that represents one tenth to one fifth of the arcuate section for the bed.

The bearing surface is, for example, a part of the support which, as a structural part, is located between the coupling and the tube. The support is preferably designed as an intermediate sheet.

The backrests are preferably provided with an arm perpendicular to their base. In particular, these arms are inserted into the receiving grooves on the front sides of the clip coupler. The supports then run with their base parallel to the pipe axis on the 6θ bed. The pipe is thus disposed along two straight lines or narrow strips, located mirror-symmetrically to the plane of symmetry of the clip.

The supports may be mounted as intermediate or intermediate sheets on the tube clip bed, for example by 65 spot welding; then simple strips without arms included are sufficient.

Radius of curvature of bearing surfaces in the coupling

SK 278379 výhodne6 preferably corresponds to 1.05 to 1.15 times the outer radius of the pipe. Due to this arrangement of the pipe in the clip coupler, the deformation of the pipe cross-section is particularly small under the action of the pressure force of the articulated support.

Also, in the area of contact between the loop loop and the wall tube, an intermediate sheet may be provided to protect the tube wall from corrosion when the tube wall is made of a material of high value as well as the loop loop material (e.g. austenitic tube wall, ferritic loop loop) .

The width of the relatively thin loop of the clip is typically several times the thickness of the tube wall W _R , namely m times, with a value of m ranging from 5 to 10. If several loops are used on one pipe clip then the width of the individual loops is reduced by a factor of 1. / n, where n is the number of loop loops.

A particularly flexible embodiment of the loop is flat iron. However, the individual loop loops may also be formed of flat wire mesh, in particular of steel wire twisted into a flat twine; this rope is soft or loose. The shape of the flat steel wire rope is advantageous compared to the shape of the round steel wire rope because the surface contact with the outer wall of the tube is considerably greater in the case of a flat shape and the temperature changes of the tube wall are transferred more quickly to the clip loop. The clip loop can also be formed from a flat sheet metal plate layer.

According to a further embodiment of the invention, the ends of the loop of the clip are each connected to a threaded pin, in particular by welding, the threaded pins passing through slots in the clip coupler arms, the clamping nuts being screwed on the undersides of the threaded pins. clamps fastened.

Clamping nuts include, in particular, spring washers, washers and special lock nuts or lock nuts. For pipes which carry a low temperature medium, for example a water pipe, holding devices which are made of a fiber-reinforced plastic material, in particular carbon fibers, are particularly preferred. In loose-bend loops, which consist mainly of sheet metal or twisted flat ropes, the wrap angle can be even greater than 180 °, resulting in an even greater friction force.

For example, the clamp pin body is connected to the loop loop.

The clip coupler arms may be flattened.

The invention, i. j. the design and dimensions of the retaining device with its tube clamp provide a clamping between the tube and the clamp, in particular having the following advantages:

a) Small preload required to establish frictional contact between the clip and the pipe wall.

b) A slight decrease in prestressing due to the compressive force of the articulated support.

c) Practically constant clamping ratios independent of different pipe diameters due to manufacturing tolerances, with the same machining.

The coupling proportions and the loop loops are stepwise adaptable to thin-walled tubes, medium-wall tubes and thick-walled tubes, so that approximately the same clamping ratios are obtained for all tube-to-clip connections. This graduation makes sense in terms of strength, since the magnitude of the forces that the holding device has to absorb in both the tensile and compressive directions is dependent on the wall thickness of the tube.

As already mentioned, more than one clip loop can be placed on one coupler, with the width of the coupler, i.e. its dimension in a direction parallel to the pipe axis, of an appropriate size, so that two pairs of notches can be placed on the coupler . It is also possible to place two couplings parallel to each other, one loop at a time, whereby a pair of support plates for the hinge pins of the hinge supports are welded over the two couplers. As a result, even higher forces can be achieved at the pipe holding point.

BRIEF DESCRIPTION OF THE DRAWINGS

BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be described in more detail with reference to the accompanying drawings, in which: FIG. 1 is a front view of a holding device according to the invention, wherein the articulated support and its anchoring on the building skeleton are omitted, FIG. 2 is a side view of the holding device of FIG. 1, with the clamping screws omitted, FIG. 3 shows a second embodiment in which the loop of the clip is clamped by means of a clamping screw with an inserted bundle of disc springs, FIG. 4 is a perspective view of a loop of a clip comprising a flat wire or a flat wire mesh, FIG. 5 shows a loop of a clip comprising a belt composed of fiber-reinforced plastic lamellas; and FIG. 6 is a loop of a clip, formed as a braided, flat, free-flexing rope and consisting of individual strands with a reinforcing fiber and a plastic sheath.

DETAILED DESCRIPTION OF THE INVENTION

The invention provides, as will be explained in more detail below, a holding device HE2 (FIG. 1), in which very high frictional forces and very low clamping deformations can be achieved at a given mounting clamping force. The friction forces between the loop 8 and the coupling 6 on the one hand and the outer circumference of the pipe 1 on the other hand remain sufficiently high during operation and prevent the pipe 1 from sliding or rotating.

In FIG. 1 to 3, a holding device HE2 is shown which corresponds to a known embodiment. The object of the invention is therefore a holding device HE2 for pipe tubes 1, which is mainly used in power plants. It can also be used, in particular, in nuclear power plants where high safety requirements are placed on pipe clamps.

The holding device HE2 consists of a coupler 6 supporting from below a tube laz of at least one loop 8, which by wrapping holds the tube 1. The ends of the loop 8 are adjustable anchored on the frames 6a, 6b for adjusting the biasing of the clip 5. The loop 8 has a thickness Ds = k. Wr and width Bs = m / n. Wr, where Wr is the wall thickness of the tube if, m, n are dimensionless factors. In this case, k is < 1, and lies in the range of between 0.1 and 0.5 and is, for example, 0.46. The width Bs is several times the thickness W _{R of the} wall of the tube 1; the factor m lies approximately in the range between 5 and 10. The factor n represents the number of loops 8 used per clip 5 of the holding device HE2.

The arms 6a, 6b of the coupler 6 preferably have the same strength as the crossbars and, as shown, are flattened on the flanks facing the pipe 1 so as to form a wedge-shaped, outwardly tapered profile. The tube 1 is supported by its outer periphery in the concave seat 13 or also in the recess of the coupling 6. The radius of curvature of the bearing surface in the seat 13 is greater than the radius of the tube 1. Between the seat 13 and the arc section 14 of the outer peripheral surface 15 the abutment strips or the abutments 16. The abutment surfaces are then not part of the bed 13, but part of the abutments 16.

The bearing surfaces extend only on the fractional portions of the arc section 14. The force action of the clamping forces is thus located on the narrowly defined bearing surfaces on the coupling 6.

The supports 16 are arranged mirror-symmetrically to each other on both sides of the plane 17-17 of symmetry (which is a vertical axis plane passing through the center of the tube 1). The plane 17-17 of symmetry is also folded through the center of the coupler 6. The magnitude of the angle 2 γ of the extension, which is defined by the axis 1 of the tube 1 as the apex and the axes 18 of both bearing surfaces or abutments 16, is preferably in the range 30 ° to 100 °; wherein the arcuate section 14 of the outer circumferential surface 15 of the seating tube 1 is correspondingly slightly larger. It is particularly advantageous, as shown, to place two abutments 16, each of which are located in the outer region of the bed 13, with an angle of expansion γ of at least 60 °. Each support 16 rests on a portion of the arc section 14 which preferably corresponds to approximately one tenth to one fifth of the length of the arc section 14. The abutment strips or the abutments 16 must not be very narrow, so that the specific pressure is not too great, the action has been defined and sufficiently localized.

The armrests 16 may be fixed in their position such that they engage the edge recesses 19 at the front of the coupler 6 with their bent ends 16a. The edge recesses 19 may be omitted when the securing of the arms 16a on the front of the coupler 6 is formed by spot welding .

The ends of the loop 8 are connected to the threaded pin 20. A very suitable connection has been shown to be a welded connection, wherein the weld seams 21 are shown. The threaded pins 20 are conically tapered on their side connected to the respective ends of the loop 8 and are in the notch 20a. at the end of the loop 8 welded. The threaded pins 20 pass through the slots formed in the arms 6a, 6b of the coupler 6, and extend beyond the arms 6a, 6b so far as to provide sufficient space for mounting the washers 23, screwing the clamping nuts 9 and the locking nuts 24. of the nuts 9 determine the operating bias in the loop 8 and thus the amount of frictional force between the loop 8 and the outer circumference of the tube 1.

In the example shown, the loop 8 is formed by a curved flat steel which is softly flexible with respect to the ratio of its thickness Ws to the wall thickness Wr of the tube 1. However, the loop 8 can also be formed from a sheet metal sheet layer. In this case, at the ends of the loop 8, the individual metal plates must be connected individually and connected to the threaded pin 20, so that the tensile force transmission is uniformly applied to all the plates, for which a weld connection is also suitable. However, the loop 8 can also be made of tensile-resistant wire mesh, in particular into a flat shape of a twisted steel wire rope. This then has the advantage that the loop is freely flexible.

Fig. 3 shows, in cross-section, a bundle of disc springs 25 inserted as compression springs between two washers 5, 23 and 26 of the clamping nuts 9. The clamping threaded pin 20 is in comparison with the embodiment of FIG. 1 is therefore reasonably longer.

Fig. 4 shows a variant embodiment in which the flat strip 82 of the loop 8 consists of a flat wire 10 mesh 29 with individual wires 30. Like the slats, the individual wires 30 are preferably made of austemtic steel, the individual wires 30 being welded equally in the weld seam 21 with each other. Such loops 8 are freely flexible due to their formation from slats or wires. It is therefore recommended that the loops 8 wrap the tube 1 at a greater angle, for example 200 °. The friction is then relatively large, but this is desirable.

In the variant of FIG. 5, a plurality of fiber-reinforced plastic lamellas 32 form a flexible multilayer lamella strip 84 loop 8. Each of the lamellas 32 comprises a tangle of carbon fibers 32. The fiber-reinforced flat strip or multi-layer lamella strip 84 may be free with its carbon 23 fibers 31. threaded ends 20, which are molded in such a way that they can be crimped onto the ends, in close connection with the carbon fibers 31, of the clamping threaded pins 20, the plastic material of these clamping threaded pins 20 being identical to the material of which the lamellas are formed

32nd

In the variant of FIG. 7, the loop 8 is formed by a knitted, flat, free-flexing rope and 35 or a flat belt 85, the individual strands 33 being formed by a fiber reinforcement 35 with a plastic sheath 34. The individual strands 33 can still be surface bonded to each other by twisting. The carbon fibers of the flat strip 85 also form an integral part of the threaded bolt 20, the plastic material of which is the same as the plastic material of the sheath 34 of the individual wires 33. In FIG. 7 is also a cross-sectional view of a single strand 33 in an enlarged scale.

Claims (11)

PATENT CLAIMS Clamping device for a pipe (1), in particular a pipe (1) of a pipe in a power plant, with a hinged support (2) which is rotatably connected at one end to an anchor (4) connected to the building frame (3) and its other end is pivotally connected to a clip (5) retaining the pipe (1), the clip (5) being formed by a spade (5) with a bed (13) positioned below the pipe (1) and equipped with an articulated clutch carrier and at least one loop (8) circumferential tube (1), characterized in that the tube (1) is supported in the bearing (13) on two bearing surfaces, said bearing surfaces extending only on a fraction of the arc section (14) of the outer peripheral surface (15) and the radius of curvature of the bearing surfaces is greater than the radius of the tube (1). Holding device according to claim 1, characterized in that the loop (8) has a thickness Ds = k. Wr and width B _s = m / n. Wr, where Wr is the wall thickness of tube (1) and (k) and (m) are factors where k <1, m> 1, where (n) is the number of loops (8). SK 278379-6 Holding device according to either of Claims 1 or 2, characterized in that two bearing surfaces are mirrored symmetrically to each other on both sides of the plane of symmetry (17-17) and have a radius of curvature corresponding to 1.05 to 1.15. a multiple of the pipe radius (1), wherein the plane of symmetry (17-17) passes through the pipe axis (1 ') and the center of the coupling (6), and that the expansion angle (2 γ) defined by the pipe axis (1') ) as the apex and axes (18) of the two bearing surfaces, lie in the range of 30 ° <2 γ <100 °, with the arc section (14) for the bed (13) being larger. Holding device according to one of Claims 1 to 3, characterized in that it comprises two bearing surfaces, each of which is located in the outer region of the bed (13), the angle of expansion (2 γ) of the bearing surfaces being at least 60 °. Holding device according to one of Claims 1 to 4, characterized in that the bearing surface extends over a portion of the arcuate section (14) which represents one tenth to one fifth of the arcuate section (14) for the bed (13). Holding device according to one of Claims 1 to 5, characterized in that the at least one bearing surface is part of the support (16) which is located between the coupling (6) and the pipe (1). Holding device according to one of Claims 1 to 6, characterized in that the bearing surface is part of a support (16) which is designed as an intermediate sheet. Holding device according to claim 7, characterized in that, in order to secure the position, the support (16) is inserted by one arm (16a) into a recess (19) on the front side of the coupling (6). Holding device according to one of Claims 1 to 8, characterized in that the ends of the loop (8) are each connected to a threaded pin (20), the threaded pins (20) pass through notches in the arms (6a, 6b) of the coupling (6) and at their ends extending beyond the underside of the arms (6a, 6b) of the coupler (6), clamping nuts (9) are screwed with which the loop (8) is biased. Holding device according to claim 9, characterized in that clamping nuts (9) are provided as means for adjusting the tension of the clip (5) and these clamping nuts (9) are provided with compression springs, in particular disc springs (25). ). Retaining device according to one of Claims 1 to 10, characterized in that the loops (8) are formed by a strip to which the clamping threaded pin (20) is connected in one piece.