EP0128176B1 - Heating chamber for continuous filaments - Google Patents

Abstract

A heating chamber for continuous filaments is comprised of two parts (98, 99) of which the congruent upper surfaces are layed one on top of the other and which delimit therebetween a filament channel (10, 19). On both sides of the filament channel tight bands (25, 35) are inserted in grooves, said bands being extended beyond the groove only by a small distance. About the filament channel, a heating area is created wherein the heating gas enters to heat up uniformly both parts.

Description

I. Technical field

The invention relates to a heating chamber for running threads. This heating chamber is suitable for the direct treatment of a thread with saturated water vapor under increased pressure. The particular problem with such heating chambers is that the heating medium, which is under increased pressure, escapes through the thread inlet and outlet in such large quantities that the operation of the heating chamber is uneconomical.

11. State of the art

To remedy this, adjustable and rigid labyrinth seals and gap seals at the thread inlet and thread outlet are already known. Labyrinth seals suitable for threading consist of a stack of mutually adjustable plates with openings. By moving the plates relative to each other, the openings can be adjusted to a large width and a small width suitable for threading (e.g. US-A-2,529,563). However, these labyrinth seals have proven to be fundamentally unsuitable, since here the necessity of an undisturbed thread run cannot be reconciled with the necessity of providing a strongly tortuous outlet path in order to avoid losses of heating medium. Gap seals are indeed suitable. With them, a large gap length causes a sufficiently large reduction in losses. However, as the gap length and the gap width increase, threading, in particular pneumatic threading, becomes an insurmountable problem. From DE-A-27 03 991 a heating chamber is known, the ends of which are closed by a bushing and a bolt fitted therein. The bolt has a thread groove on a surface line through which the thread runs during operation. To thread the thread, the bolt is removed from the socket.

This heating chamber has obvious operating disadvantages. A major disadvantage is that the bolt for sealing the thread guide groove and the parting line between the two surfaces must be fitted very tightly into the bushing, so that it is jammed therein, particularly when it cools down.

Remedial action has been attempted by sealing a body provided with a thread groove on its flat surface with a heat-resistant sealing plate and a solid cover lying thereon. Here, the heating chamber was tight at low pressures. At higher pressures, however, considerable contact forces had to be applied and there were problems with the thread running. Above all, stable operation of the heating chamber is not possible. The instability was particularly evident from the repetitive, sudden emission of steam and temperature fluctuations. The temperature and the uniformity of the temperature of the running thread were unsatisfactory.

111. The invention

Surprisingly, this problem could be solved by the measure specified in claim 1. Due to the sealing strips provided according to this invention, which extend along the thread channel and at a certain distance from it, the thread channel is still closed by the closing surfaces. However, the contact pressure with which the closing surfaces lie on top of one another, as well as the manufacturing tolerances, can be significantly lower. It does not matter whether the closing surfaces touch each other sealingly. An emerging joint allows the saturated steam to penetrate as far as the sealing strips, with the result that the condensing saturated steam in a region surrounding the thread channel leads to heating of the 'two bodies of the heating chamber. In addition, the parting line is so narrow, even with low contact pressure, that convection and radiation also contribute significantly to the heat transfer between the metallic closing surfaces, if and insofar as there is not even contact between the closing surfaces and direct heat conduction.

The solution according to the invention shows that the previously used idea of closing the thread channel or the surface warp of one body leading the thread absolutely tightly laterally by the closing surfaces of the other body was wrong. Because with metallic contact, tight tolerances would be required, which cannot be achieved due to the thermal expansion. When sealing with a flexible sealing plate, which also acts as insulation, it is completely prevented that the two bodies of the heating chamber heat up evenly. In both cases, the saturated steam supplied to the narrow thread channel with its only limited surface area is not able to heat the side walls of the heating chamber to a sufficient extent. Cold areas therefore form, in which condensate collections occur, which periodically evaporate explosively.

By the seal according to the invention, in contrast to the solution previously used, it was also avoided that the inevitable impurities in textile operation such. B. thread remnants, dried or cracked finish u. lead to leaks.

It has also been shown that previously used preheating channels that extend along the thread groove are not sufficient, both massive body that surround the thread channel to heat to a uniform temperature. Rather, this could only be achieved through the invention.

The distance of the sealing strips from the thread channel depends on the size of the body that forms the heating chamber and must be heated. The larger these bodies are, the greater this distance should be. In the case of a heating chamber, the cylindrical inner body of which is surrounded by a cylindrical outer body as a jacket and which has a diameter of 50 mm, the distance of the sealing strips from the thread channel was 1/10 of the diameter.

The solution according to the invention is supported in that at least one of the bodies is also subjected to a pressure cushion of the saturated steam from its rear side. This is particularly advantageous if the heating chamber consists of an outer jacket and an inner cylinder with a thread guide groove enclosed by the latter. In this case, the movable outer jacket and the inner cylinder are heated evenly on two sides of their circumference.

Sealing strips are also provided at a distance from one another on the back of the body. The area circumscribed by these sealing strips is heated up. To exert the contact pressure, this area is larger than the area circumscribed by the sealing strips on the heating side, so that the pressure pad of the heating gas / saturated steam simultaneously causes pressure and heating of the two bodies.

As already mentioned, the parting line between the closing surfaces of the two bodies remains so narrow that only insignificant amounts of steam escape through this parting line in the thread running direction. A transverse seal is provided at the thread entrance and / or thread exit. This cross seal can, for. B. are formed in that the sealing strips have extensions at their ends, which extend to the thread channel or up to close to the thread channel. In another embodiment, the transverse seals are designed as sealing strips, into which a thread groove is cut, which, moreover, is caused by the running thread itself when the sealing strips are made from a rubber-like material.

If the thread guide groove is formed in insert pieces which are inserted into an insert groove of one body, the insert groove is accompanied on both sides by sealing lips. In an advantageous embodiment, the insert pieces are clamped into their insert grooves by means of the sealing strips, the sealing lips then having a double function. In this embodiment, it is furthermore expedient and advantageous to apply steam to the inserts from their underside, which results in a further standardization of the temperature in the region of the thread channel.

As already mentioned, the sealing strips are preferably made of an elastic material. They are inserted into grooves in one of the bodies that form the heating chamber. They protrude slightly above the top edge of the groove. The difference between the groove depth and the thickness of the sealing strips is preferably not greater than the elastic deformability of the sealing strips under the contact pressure provided for the operation.

The material of the sealing strips (sealing lips) is also sufficiently heat-resistant.

To replace the sealing strips, it is expedient to design the sealing strips in one piece, in particular in the form of a ring. In this case, the groove of the thread channel is preferably formed as a rectangular window with the narrow sides in the thread entry area and thread exit area. However, the sealing strips can also be designed as a rectangular window.

In another embodiment, in which the heating chamber consists of an inner cylinder on the one hand and an outer cylinder enclosing this as a jacket, the sealing lips are formed in that the outer body is divided in a radial or secantial plane and in that a sealing plate is inserted in this longitudinal plane, which is deformed by tightening the two halves of the outer body so that one end edge lies sealingly against the inner cylinder. The division plane is preferably between the center of the inner cylinder and the thread groove in the inner cylinder, so that the end edges of the sealing plates form sealing lips on both sides of the thread channel. In the case of a profiling of the inner body and outer body z. B. by a thread, the sealing plate is preferably inserted and braced before cutting the profile in the outer body and only then the profile is introduced so that the sealing plate adapts to the profile.

The heating chamber to which this invention is applied in any case consists of two bodies which, when in operation, have surfaces which are congruent in shape (sealing surfaces) and which form a separating joint. At least one of the surfaces has a surface distortion (surface deformation) which forms a thread channel, the cross-section of which is closed by the other closing surface. The surface deformation can be formed as a groove in the one body. In this case, the surface deformation of the other body can also be a groove. The groove can preferably be formed on the surface line or screw line of an inner cylinder, which is enclosed by an outer cylinder as a jacket, the outer cylinder also having a groove on a surface line or screw line of its inner circumference, which preferably has a larger cross section than the first groove. If the grooves are covered in the threading position, an enlarged threading opening is created. By relative rotation of the jacket, the thread groove in the inner cylinder is ver closed.

A preferred embodiment consists of an inner cylinder with a groove and an outer cylinder which is slotted along a surface line. If the slot covers the groove of the inner cylinder, an insertion gap is created for a running thread.

It should be noted that the surface deformations, i.e. H. Grooves or steps can be rectilinear or curved so that the thread is guided without contact or in contact with the surface warp. Likewise, the surfaces can be flat or slightly curved in the direction of the thread.

The thread heating chamber according to the invention can in operation, in particular at the thread entrance and / or thread exit to a small gap width of z. B. 0.2 to 0.5 mm width can be set so that a running thread can be guided undisturbed, but the losses of the heating medium are low. The gap width, in particular in the thread outlet area, can differ over the gap length.

The two-part filament heating chamber can also be provided with recesses in the central region of its gap length, so that the clear width of the gap widens here. On the one hand, this can be useful in order to allow a certain ballooning of the thread and / or to avoid or reduce wall friction of the thread.

IV. Commercial usability

When heating above 100 ° C, there is the advantage of direct heat treatment of a running thread, in particular multifilament chemical thread, with the heating gas in the good heat transfer. Saturated water vapor has the advantage of high latent heat content (heat of vaporization) over superheated steam or hot air. Direct saturated steam treatment leads to a strong heating of the thread at high thread speeds and short dwell times due to the very high heat transfer coefficients in the case of condensation - in contrast to convection, radiation or direct heat conduction. Saturated steam treatment also results in a uniform temperature distribution and good temperature stability over the entire length of the treatment section. The treatment path can also be specified as desired by connecting several treatment chambers in series, since the required uniformity and constancy of the treatment temperature for several treatment chambers can be ensured by adjusting the pressure and by pressure equalization between the treatment chambers - with simultaneous removal of inert components. The losses at the entrance and exit of the treatment section can be kept low and lower than with comparable air heating sections if the thread entry and thread exit locks are designed accordingly.

Therefore, the saturated steam treatment chambers according to the invention are suitable in the case of the simple threading of running threads according to the invention, in particular for those thread treatment chambers in which a large amount of heat must be transferred to the thread at a high thread speed within a relatively short dwell time, as is the case, for. B. in the case of synthetic fibers in spinning processes, spin-stretching processes, spin-texturing or spin-stretch texturing processes and stretch-texturing, draw-twist, stretch-winding and other stretching processes is the case.

It is possible to align several such filament heating chambers parallel to one another and to connect them to one another by means of a single line for the saturated steam. Throttle losses between the thread channels are largely avoided and a good consistency of the thread temperatures achieved is guaranteed from one thread run to the other.

Likewise, several threads can be guided in one thread channel. Furthermore, it is also possible to have several surface faults, e.g. B. groove to provide, with one or more threads are guided in each groove. These several grooves are then between two sealing strips which are arranged at a distance from the outer grooves, which is particularly important for the temperature accuracy and the operating behavior of the outer grooves.

In a preferred embodiment, the filament heating chamber is made on both sides by forming a filament heating chamber on both sides of a central plate.

V. Implementation of the invention

Exemplary embodiments of the invention are described below.

• Figur 1 eine aus ebenen Platten bestehende Heizkammer, deren Fadennut längs und quer von Dichtleisten eingerahmt wird ;
• Figur 2 eine aus ebenen Platten bestehende Heizkammer, deren Fadennut in Längsrichtung von Dichtleisten begleitet wird ;
• Figuren 3a bis 3c eine aus aufeinander gleitenden Platten bestehende Heizkammer ;
• Figuren 4, 5, 6 eine aus Innenzylinder und Außenzylinder bestehende Heizkammer mit einer Fadennut im Innenzylinder und einer Einfädelnut im Außenzylinder ;
• Figuren 7, 8, 9 eine aus Innenzylinder und Außenzylinder bestehende Heizkammer mit einer Fadennut im Innenzylinder und einem Einlegschlitz im Außenzylinder ;
• Figuren 10 bis 14 eine aus Innenzylinder und Außenzylinder bestehende Heizkammer mit Einsatzstücken im Innenzylinder ;
• Figuren 15, 16 a/b eine aus gestuften, relativ zueinander verschiebbaren Platten bewegliche Heizkammer ;
• Figuren 17a bis c Abdichtung der Enden einer Heizkammer.

Show it

• 1 shows a heating chamber consisting of flat plates, the thread groove of which is framed longitudinally and transversely by sealing strips;
• Figure 2 is a heating chamber consisting of flat plates, the thread groove is accompanied in the longitudinal direction by sealing strips;
• Figures 3a to 3c a heating chamber consisting of sliding plates;
• Figures 4, 5, 6 a heating chamber consisting of an inner cylinder and an outer cylinder with a thread groove in the inner cylinder and a threading groove in the outer cylinder;
• FIGS. 7, 8, 9 a heating chamber consisting of inner cylinder and outer cylinder with a thread groove in the inner cylinder and an insertion slot in the outer cylinder;
• FIGS. 10 to 14 a heating chamber consisting of inner cylinder and outer cylinder with inserts in the inner cylinder;
• FIGS. 15, 16 a / b a heating chamber which can be moved from stepped plates which are displaceable relative to one another;
• Figures 17a to c sealing the ends of a heating chamber.

16 to 16, the pressurized heating chamber according to this invention is formed over its entire length by only two bodies, which likewise form the central heating region and the sealing end regions of the heating chamber.

Their advantage is in particular that the thread can be threaded easily, quickly and safely and that the sealing system, in particular the sealing strips between the closing surfaces of the body of the heating chamber, results in a complete seal on the one hand and good heat management on the other. The problem-free threading and sealing made it possible to make the narrow, gap-like end areas very narrow - limited only by the thread titer - and as long as desired. This almost completely prevents steam from escaping. Vapor pressures of saturated water vapor with temperatures up to over 200 ° C as well as a steady increase of the vapor pressure from atmospheric pressure up to operating pressure and the steam temperature for the incoming thread and a steady decrease of the pressure up to atmospheric pressure and the temperature for the outgoing thread are made possible. The steady decrease in steam pressure also eliminates the risk of steam flow damaging the thread.

The heating chamber according to this invention is used in particular for the direct heating of a running thread by means of a saturated water vapor. Therefore, in the context of this application, one speaks primarily of saturated steam.

Fig. 1 shows a heating chamber, which consists of the two flat plates 98 and 99. We look at the closing surfaces of the two plates. In the operating position, these closing surfaces, which are congruent in terms of their shape, lie on one another under a pressing force. A wide groove (insert groove), into which insert bodies 4 are inserted, is introduced into the plate 98. Each of these insert body 45 has thread channels 10, the width of which is adapted in the end regions of the heating chamber to the thickness of the thread to be treated and z. B. 0.2 mm for a thread of 167 dtex. The insert pieces are surrounded by the longitudinal seal 35 on both sides and by a transverse seal 34 at the ends. The plate 98 is penetrated by the bore 27, which serves as a steam supply channel. The central region of the thread guide groove is connected to this steam supply channel by bores 48.

The plate 99 is connected to the plate 98, e.g. B. connected by a hinge (not shown here) so that it is pivotable in the direction of arrow 100. In the closed position, the thread guide grooves 10 and 19 form a thread treatment chamber which, for example, through the steam supply channel 27. B. can be loaded with saturated water vapor.

It should be mentioned that the inserts are arranged at a distance from one another, so that extensions 101, 102 form between them. However, the inserts can also lie close to one another, and their main advantage is that they can be mass-produced cheaply and easily replaced when worn or - when the thread titer to be processed changes - can be replaced by inserts with other channel widths. The mouths of the thread guide grooves 10 of each insert 45 - seen in the direction of the outflowing steam - are rounded off so that the flow energy of the steam flow deflected by the Coanda effect is repeatedly destroyed by impact on the side wall of the next insert.

2 illustrates that sealing lips 25 extend in the parting line between the closing surfaces of the two bodies on both sides of the thread guide groove 10, 19. The length of the sealing lips is preferably almost equal to the length of the thread guide groove. However, it can also be slightly shorter. The sealing lips are inserted in grooves so that they do not fall out when the thread heating chamber is opened and do not move in the parting line when the body moves relative. The longitudinal movement of the sealing lips is prevented by the fact that the sealing lips have extensions 120 at their two ends, which are inserted into corresponding extensions of the grooves. This avoids thermal changes in length in particular. Furthermore, the extensions at least partially seal the parting line between the bodies in the direction of the thread entrance and thread exit. The grooves with their sealing lips are preferably located in the stationary body, which in turn is preferably the thread-guiding body.

In Fig. 3a, a heating chamber is shown in cross section, which also consists of two flat plates 51 and 53. These plates are displaceable relative to one another parallel to their surface by cylinder-piston unit 69-71. In one end position, the front edge 105 of the plate 51 recedes behind the thread guide groove 10, so that an opening is created in which the thread can be laid. In the other relative position shown in dashed lines, the thread guide groove is closed. In the closed state, the thread guide channel 10 is supplied with saturated steam via bore 58 by opening a valve (not shown here) via steam feed line 80. The back of plate 53 is also charged with steam through bore 103. As a result, the plate 53, which is sealed off from the housing 104 by circumferential seals 49, is pressed against the other plate 51, so that these plates, at least their seals 56, lie on one another in a vapor-tight manner. It is particularly important that the area circumscribed by the surrounding seals 49 is larger than the area formed by the longitudinal seals 56, 57 and the associated transverse seals.

Fig. 3b shows a similar embodiment, the differs from that in Fig. 3a in principle only in that the front of the plate 51 is provided with a step 108.

The embodiment according to FIG. 3c is also essentially similar. Its main difference from the embodiments according to FIGS. 3a and 3b is that the plate 51 in one end position does not open a threading slot above the thread guide groove, but rather has an enlarged longitudinal groove 109 which, in the position shown, in which the heating chamber is not in operation, also the thread guide groove 10 is aligned and forms an enlarged threading gap through which the thread can be threaded pneumatically or by means of bristles. The threading groove 109 is provided on one side with a bevel so that the thread is pressed into the thread guide groove 10 by the bevel when the plate 51 is moved into its operating position shown in dashed lines.

In all of these exemplary embodiments, it is necessary that the housing 104, which surrounds the plates 51, 52 forming the heating chamber on at least two opposite sides, in the case of the exemplary embodiment according to FIG. 3c on all sides, is designed to be stable and rigid enough to absorb the steam forces and ensure, even when loaded with the steam pressure, that the plates lie close together in their contact surfaces (closing surfaces) and with their longitudinal and transverse seals.

The exemplary embodiment according to FIGS. 4 to 6 has the inner body 6, which is fixedly connected to the flange 3, and the outer body 4 with a handle 13, which is rotatably arranged around it.

Over its entire length, the inner cylinder 6 has the groove 10 (thread groove) which serves to guide the thread and which forms the thread channel in the operating position. This thread groove 10 is expanded in the central region 19 in the circumferential direction (width) and in depth, so that there the thread can move, swing, and balloon without touching the walls, but in which the saturated steam in particular is under a uniform pressure and therefore also has a uniform temperature.

The outer cylinder 4 has a groove 11 which is made in the inner jacket and the flanks 12 of which run gently from the bottom of the groove onto the inner jacket.

The flange 3 has a hole 20, the front region 21 of which in the top view according to FIG. 5 covers the thread guide groove 10. The flanks 22 of the hole 20 are therefore flush with the flanks of the thread guide groove 10 in the top view according to FIGS. 5 and 6.

The outer cylinder 4 is divided and is clamped by the flanges 23 and screws 24 such that the inner jacket closes tightly around the outer jacket of the inner body 6. In the parting plane of the divided outer body 4, an elastic spacer plate 26, for. B. sealing plate.

Longitudinal seals 25 designed as sealing strips are provided on both sides of the thread groove 10 in the inner cylinder 6, which seal the thread groove 10 and also its central region 19 in the circumferential direction.

The inner cylinder 6 has a central bore 27 serving as a preheating channel, which is closed at the top and communicates downward with the connecting pipe 28. Through the connecting pipe 28, the bore 27 is charged with a pressurized heating gas, in particular saturated steam. The preheating channel 27 is connected to the thread groove 10, in particular its central region 19 through holes 29.

In operation, an axial force is applied to the outer cylinder 4 in the direction of arrow 30. A trapezoidal thread 31, which is attached in the upper region of the outer cylinder 4 and inner cylinder 6, is used for this purpose. By turning the outer cylinder 4 relative to the inner cylinder 6 by means of a handle 13, the outer body 4 is pressed against the sealing plate 8 on the end flange 3 in a sealing manner. In this rotational position (operating position), the groove 11 of the outer body 4 has the position shown in FIG. 6. The groove 11 is therefore behind the sealing lips 25, so that no pressure medium, heating gas, saturated steam can get into the groove 11 from the thread groove 10. The thread groove 10 is limited by the inner wall of the outer cylinder 4 to a very narrow gap, which prevents the uneconomically large amounts of the pressure medium from escaping. Gap widths are on the order of less than 0.5 mm.

By turning the outer cylinder into the position shown in FIG. 5 (threading position), the groove 11 of the outer cylinder is brought into a position in which it - in the vertical direction - the hole 20 in the flange 3 and - in the radial direction - the thread groove 10 covered. This creates a large threading opening through which the thread can be threaded pneumatically or by means of a bristle or similar means. The angle of rotation of the outer cylinder is greater than half the central angle (central angle) between the sealing strips 25.

The exemplary embodiment according to FIGS. 7 to 9 largely corresponds to that shown in FIGS. 4 to 6. The heating chamber consists of a tubular inner cylinder 6 with thread groove 10. The thread groove 10 is narrow in the thread inlet part 1 and in the thread outlet part and widens in the central region 19. The inner cylinder 6 is fixed in place on the flange 3. Its central bore, which serves as a preheating channel 27, is connected to steam line 28 with saturated water vapor. The water vapor can escape through the holes 29 into the enlarged central region 19 of the thread groove 10. The inner cylinder 6 is surrounded by an outer cylinder 4, which has an insertion gap 32 (slot) for the thread. The outer cylinder 4 is surrounded by bandages 33 to increase the strength. The outer cylinder 4 can be rotated by means of a handle 13.

In the position shown in FIG. 8 (threading position), the insertion gap 32 opens radially on the thread groove 10. It should be mentioned that the insertion gap 32 can also be directed secantially to tangentially. In the second rotary position (operating position) shown in FIG. 9, the jacket is rotated so that the thread groove 10 is covered by the inner circumference (closing surface) of the outer cylinder 4 and thus forms the thread channel.

A further special feature compared to the exemplary embodiment according to FIGS. 6 to 6 is that the inner cylinder 6 also has the transverse seals 34 at the thread inlet and thread outlet in addition to the longitudinal seals 25. These cross seals can be O-shaped sealing strips that extend from one longitudinal seal to another. However, it can also be an O-ring which surrounds the entire inner part 6. Likewise, the sealing strips 25 and transverse seals 34 can be formed in one piece as a ring or rectangular window. The sealing strips and cross seals are placed in the grooves of the inner cylinder (or the outer cylinder) so that they do not slip due to the relative movement of the cylinders. The grooves are only so deep that the sealing strips protrude beyond the closing surface of one body and lie in the operating position of the two bodies in a sealing manner on the closing surface of the other body (applies to all exemplary embodiments).

By using the transverse seals 34 according to the exemplary embodiment 7 or 10, it becomes superfluous to press the outer jacket 4 against the sealing plate 8 by axial force, as is shown in FIG.

Furthermore, the inner cylinder 6 has on its rear side the longitudinal seals 35 shown in FIG. And FIG. And - in each case at the thread inlet and thread outlet - a transverse seal not visible here (corresponding to the transverse seals 34 on the front side). The area between these longitudinal seals 35 and their transverse seals is charged via line 36 with the heating medium, here the saturated steam from tube 27. Since the secantial distance between the longitudinal seals 35 on the back of the inner cylinder 6 is greater than the secantial distance of the sealing strips 25 on the front of the inner part 6, in the operating position according to FIG. 9 the vapor pressure presses the movable outer cylinder 4 against the longitudinal seals in the direction of arrow 37 25 on the front. On the one hand, this results in a secure sealing of the thread groove 10 and the surface area circumscribed by the sealing strips 25 and the transverse seals 34. Above all, however, the heating gas / saturated steam cushion on the back serves for the additional heating of both the inner and especially the outer cylinder. 10 to 12, the cylindrical inner part 6 (inner cylinder) is in turn firmly attached to the flange 3. The outer part 4 is again designed as a rotatable jacket 4 (outer cylinder) provided with an insertion gap 32. The insertion gap 32 opens into the thread groove 10 in the one rotational position (threading position) (not shown). In the other rotational position shown in FIGS. 11 and 12 (operating position), the jacket 4 covers the thread groove 10.

A groove 38 (insertion groove) running through from top to bottom is made in the inner cylinder 6 and preferably has the same width and depth over its entire length. Insert pieces 39 and 40 are inserted into the groove 38. The inserts 39 form the thread entry part and thread exit part and have a narrow thread groove 10, as shown in FIG. 11. The insert part 40 forms the central region 19 of the thread guide groove and can accordingly have a thread guide groove with an enlarged cross section, as shown in FIG. 11. The inserts 39 and 40 are sealed along their entire length by longitudinal seals 25 on both sides of the groove. The flanks of the insert pieces are sealed on both sides by sealing strips 41 with respect to the insert groove 38. In order to achieve a certain sealing mobility, the flanks of the insert groove and the insert parts are aligned parallel to one another.

The insert 40 of the central area 19 has on its rear side a longitudinal groove 42 which is penetrated by the holes 29 through which the thread groove 10 of the central area 29 is connected to the central bore 27 serving as a preheating channel for steam supply. Since the secantial distance of the sealing strips 25 on the thread groove side of the insert parts 40 is smaller than the secantial distance of the sealing strips 41, the insert piece 40 is pressed against the inner circumference of the jacket by the vapor pressure.

The insert pieces 39 have the transverse seals 34 already described for the exemplary embodiment according to FIG. The inserts 39 at the thread inlet and thread outlet can, but do not have to, be provided with a longitudinal groove 43 on their rear side which is acted upon by steam pressure. Likewise, it is not absolutely necessary to provide a separate steam duct for steaming the longitudinal groove 43. Rather, the vapor pressure from the longitudinal groove 42 of the insert 40 will provide sufficient vapor pressure also on the back of the insert 39. Even if the longitudinal groove 43 is not present or extends over only a short area from the insert 40 to the thread inlet or thread outlet, the vapor pressure forming behind the insert 39 is sufficient for the sealing lips 25 to be sufficiently pressed against the inner circumference of the jacket 4 to worry. It should be taken into account that a flow in the thread channel corresponding to the pressure drop occurs in the thread inlet and thread outlet, so that the static pressure on the back of the insert 39 is greater than the static pressure on the front of the insert. Otherwise, the sealing strips 41 also ensure that the rear side is vapor-tight in the case of the insert pieces 39 is completed.

As can be seen from FIG. 10, the end faces of the insert groove 38 are sealed by the sealing plates 44 which are tightly fitted and sealed into the insert groove 38 at the ends. Sealing plates can also be used which lie tightly on the end faces of the inner cylinder.

In the exemplary embodiment according to FIGS. 13, 14, in particular the thread inlet part and the thread outlet part of the heating chamber are formed by a plurality of relatively thin insert pieces 45. For this purpose, the inner part 6, as also shown in FIGS. 7 and 10, has an insert groove 38. The flanks of this insert groove 38, as can be seen in FIG. 14, are shaped in a converging manner in such a way that they provide support on both sides of a sealing lip 25 .

The heating chamber can also consist of an insert 40 in its central region. It can be seen that this insert 40 is also missing or can be replaced by individual shorter inserts.

The inserts 45 and 40 have flanks which are also adapted to the sealing lips 25. As a result, the inserts can be clamped between the sealing lips 25. Since there is a distance between the sealing lips, a static pressure will be established below the sealing lips, while a flow will arise above the sealing lips with a corresponding reduction in the static pressure. As a result, the sealing lips in this exemplary embodiment are also pressed forward against the inner circumference of the jacket 4. The insert parts can consist of particularly wear-resistant materials in the exemplary embodiments according to FIGS. 10 to 14, such as, for. B. ceramic, in particular sintered ceramic or sintered metal. The advantage of this design is that the inserts can be easily removed when the thread titer to be machined or changed. Furthermore, the inserts are easy to manufacture in bulk, while the manufacture of a wide groove in the inner cylinder 6 requires less manufacturing effort than the manufacture of a very fine thread groove.

A double filament heating chamber is shown in FIG. The filament heating chambers consist of plates 51, 52 and 53. The plate pair 51 and 53 and the plate pair 52 and 53 each form a filament heating chamber.

Each plate 51 and 52 has the two planes 73 and 74 which are plane-parallel to one another and are connected to one another by a step 54. The plate 53 is displaceable between the plates 51 and 52. The plate 53 also has the plane-parallel planes 75 and 76, which are connected to one another by the steps 55. The steps 54 and 55 of the plates 51, 52 and 53 are each of the same size. In the exemplary embodiment it is shown that the steps form a plane. However, a different level training is also possible. In particular, it is possible to make the steps concave - in the cross section shown. It is also possible to slightly bend the steps in the thread running direction so that the thread is guided in contact with a step. Likewise, curved surfaces can be provided instead of the planes in the thread running direction, so that the thread is guided in contact with a surface. In both cases, a curved thread channel is created.

The plate 53 is slidably guided with its levels 75, 76 between the mutually facing levels 73, 74 of the plates 51 and 52. In the position shown in FIG. 17 (threading position), a longitudinal slit is created on the front of the plates 51 and 52 in the area of the steps 55 of the plate 53, since this step 55 slightly projects above the front of the plates 51, 52. Through these longitudinal slots, a thread running parallel to the longitudinal slots can be inserted transversely to its running direction into the gap between the plates 51 and 53 or 52 and 53. The plate 53 is then moved back into a position which is shown in FIG. 16a (operating position). In this position, two narrow, parallel, straight or possibly curved thread channels are created. Each thread channel is formed by the plane 74 and the step 54 of the plate 51 and 52 and by the plane 75 and the step 55 of the plate 53. The two thread channels are fed with saturated water vapor through steam connection 61 and channel 58 and intermediate channel 60. For this purpose - as can be seen from FIGS. 16a, 16b - in the area of the mouth of the steam channel 58 and the steam passage channel 60, a recess 77 is machined into the plane 74 and the step 54 of the plates 51 and 52, respectively. This recess causes an expansion of the thread channel. In this case, this expansion serves to allow the steam flowing through steam channel 58 to flow unthrottled into channel 60, so that the same pressure and temperature conditions exist in the two adjacent thread channels. However, it is also possible to provide the recess 77 over a greater length, so that the narrow gap only remains in the inlet and outlet region of the thread 59. It should be mentioned that the gap width there is approximately 0.2 to 0.3 mm with a length of the end regions of 60 mm and more. This means that a thread of 167 dtex can be treated with saturated water vapor without damaging wall friction with only slight steam losses at temperatures of 220 ° C, corresponding to a pressure of 24 bar.

The plate pack consisting of plates 51, 52 and 53 is surrounded on all sides by insulating material 62. This plate pack is enclosed in a solid block (housing), which is screwed together from the plates 64, 65, 66 and is stable enough to absorb the pressures arising in the interior of the thread channel and the forces caused thereby. In order to compress the plate pack, the hose / expansion body 68 is nestled into a chamber 67 of the plate 66, which extends essentially over the entire length of the heating chamber. The hose has be preferably an elongated cross section, so that the width with which the hose rests on the side surface of the plate 52 is greater than the width of the thread channel in the operating position. The hose 68 can therefore be subjected to a pressure that is approximately lower by the area ratio in order to compress the plate pack 51, 52, 53 in a vapor-tight manner.

The hose 68 is either connected to the company compressed air network. However, it is preferred to connect the hose 18 to the line network of the heating gas. You can do this e.g. B. fill the hose 68 with a liquid which in turn is acted upon by the pressure of the heating medium. To achieve the previously described advantages of additional heating, especially the plate, which has no preheating channel. the hose is preferably charged with the heating gas itself.

The balls 63 transmit the forces applied to the plate pack 51, 52, 53 by the hose to the plate 64 of the solid block.

To seal the thread treatment chamber there is at least one sealing strip 56 or 57 on each pair of levels, which is flexible within limits. By means of these sealing strips it is avoided that the surface pairing 73, 74 of the plate 51 and the surface pairing 75, 76 of the plate 53 have to be manufactured with absolutely exact dimensional accuracy.

The middle plate 53 is adjusted by the cylinder-piston unit 70, 71 by means of the piston rod 69. With 72 a stop screw is designated, through which the gap width of the thread treatment chamber can be adjusted during operation. 17a-17c, the heating chamber 2 with the thread inlet 1 is shown in longitudinal and cross-section. It should be mentioned that the thread outlet end of the heating chamber can be designed accordingly. The steam supply channel into the heating chamber 2 is not shown. Saturated steam is used under a pressure of, for. B. 20 bar, so that a saturated steam temperature of about 210 ° C.

An outer body 4 (outer cylinder) is placed on the end flange 3 of the heating chamber 2. The outer body 4 is tightly clamped to the end flange 3, but - as will be explained later - a certain relative movement is possible. A seal (not shown here) can be placed between the end flange 3 and the outer body 4.

An inner body 6 is located in the inner bore 5 of the outer body 4. This inner body 6 is designed as a cylinder (inner cylinder) with a trapezoidal thread 7. The inner bore 5 of the outer cylinder has a meshing thread. The inner cylinder 6 with its thread is adapted to the inner bore 5 with its thread as tightly as possible. The sealing plate 8 is located at the bottom of the bore 5. It can be the same sealing plate. which is also placed between the end flange 3 and the outer body 4 for the purpose of sealing.

As can be seen in particular from FIGS. 17b and 17c, the end flange 3 has a hole 9 through which the thread emerges from the heating chamber. A corresponding hole is in the sealing plate 8. The jacket of the bore 5 in the outer body 4 cuts - seen in the projection onto a plane - this hole and has a groove 10 which - in the radial direction - extends through the thread of the bore into extends the core and is aligned in the longitudinal direction with the hole 9 of the end flange. This groove 10 is provided as a thread guide groove (thread groove). The inner cylinder 6 has - as can be seen in FIG. 1 - a corresponding groove 11. This groove 11 only extends to the core of the inner cylinder 6. However, it can also extend into the core. The flanks 12 of the groove 11 are flared in the circumferential direction. The inner cylinder has a handle 13 with which the inner cylinder 6 can be rotated relative to the outer cylinder 4.

In the rotational position, which is shown in Fig. 17b (threading position), the thread groove 10 in the inner jacket of the outer body 4 and the groove 11 in the thread and possibly the core of the inner body 6 (threading groove) form a wide threading slot through which the thread can be threaded. For pneumatic threading, the inner wall of the heating chamber 2 runs in a funnel shape towards the hole 9 in the end flange 3.

By turning the inner body 6 in the direction of the arrow, the threading groove 11 in the inner cylinder 6 is rotated into the position (operating position) shown in FIG. 3. As a result, the thread groove 10 serving for thread guidance is reduced to a narrow gap, the width of which is so small that the heating gas or saturated steam losses and pressure losses are small. Because the flanks 14 of the thread groove 10, which are cut into the thread of the outer body, run essentially radially and because the flanks 12 of the threading groove 11 in the inner cylinder are widened in a funnel shape, the thread is twisted along the flanks when the inner cylinder 6 is rotated 14 transported into the thread groove 10 serving the thread guide.

As can be seen from FIGS. 15b and 15c, the outer body 4 is divided in a plane which lies between the center 15 of the inner cylinder 6 and the thread groove 10 in the outer body. A seal 16 is inserted into the parting plane, which is elastic and thicker than the spacers 17 in the relaxed state. The two halves of the outer body are clamped together by screws 18 after the seal 16 and the spacers 17 have been inserted beforehand. Only then is the thread cut into the bore 5 of the outer body 4. This also provides the seal 16 with a thread. This has the effect that the seal seals the thread with the core and flanks on both sides of the thread groove 10 as a sealing strip. To the required relative movement of the two halves of the To allow the outer body 4 on the end flange, the flange screws in the elongated holes of the end flange 3 are slightly movable. The spacers 17 can be made of a relatively soft metal, so that it is also possible to readjust the seal by pressing the spacers together. The spacers can also be missing. Your advantage is initially only that the seal is set independently of the fitter during assembly.

By rotating the inner cylinder 6 relative to the outer body 4, the overlap of the grooves 10 and 11 is eliminated on the one hand, the groove 11 being rotated so far that it lies on the other side of the sealing plate 16. On the other hand, this rotation causes the inner body 6 to be screwed into the outer body 4, in such a way that it lies against the sealing plate 8 in a sealing manner with an axial force.

Claims (16)

1. Heating chamber for threads in motion, in particular synthetic threads, charged with saturated steam at a higher than atmospheric pressure, in particular saturated steam at a pressure of more than 2 bar, and composed of two bodies which are displaceable relatively to one another between an operating position and a threading position and which in their operating position are in sealing contact with each other over their substantially congruent surface regions (closing surfaces) and enclose between them a thread channel which is narrow at its end region and which is charged with saturated steam and through which the thread runs, characterised in that along each of the two sides of the thread channel (10) a sealing strip (25) is arranged on one of the bodies (4 or 6 ; 98 or 99) so that in the operting position of the two bodies each sealing strip makes sealing contact with the closing surface of the other body and the sealing strips between them form a flat heating zone between the two bodies, which zone is bounded by the sealing strips and encloses the thread channel over the major part of its length and is bounded by transverse fields in the thread inlet region and/or the thread outlet region.

2. Heating chamber according to claim 1, characterised in that the transverse seals are sealing strips (34).

3. Heating chamber according to claim 2, characterised by a groove for the thread in the transverse seals (34).

4. Heating chamber according to claim 1, characterised in that the transverse seals are formed by increases in width (120) at the ends of the sealing lips (25).

5. Heating chamber according to one of the claims 1 to 4, characterised in that the thread channel (10) is formed in an insert member (39, 40, 45) which is inserted in an insert recess (38) of the body (6), which recess has sealing lips along both sides.

6. Heating chamber according to claims 1 to 4, characterised in that a thread channel (10) is formed in an insert member (39) which is inserted in an insert recess (38) of one of the bodies (6) and in that the insert member (39) has lateral concavities on each side, and in that the sides of the insert recesses have concavities curved in opposite directions with a sealing strip (25) inserted therein and in that the insert member bears with its lateral concavities against the sealing strips.

7. Heating chamber according to one of the claims 1 to 6, characterised in that the sealing strips (25) are inserted in recesses of the closing surface of one of the bodies (4, 6 ; 98. 99), the depth of which recesses in slightly less than the thickness of the sealing strips, the difference being preferably within the region of the elastic deformability of the sealing strips.

8. Heating chamber according to claim 7, characterised in that the recess receiving the sealing strips (25) forms a rectangular window surrounding the thread channel (10).

9. Heating chamber according to claims 1 to 7, characterised in that the sealing strips form rectangular windows.

10. Heating chamber according to one of the claims 1 to 9, characterised in that the thread channel (10) consists of a recess in the closing surface of the first body (4), which recess is closed off by the closing surface of the other body (6) in the operating position.

11. Heating chamber according to claims 1 to 9, characterized in that in the operating position, the thread channel (10) is formed by a step in the closing surfaces of the first body (plate 51) and a congruent step in the closing surfaces of the second body (plate 53).

12. Heating chamber according to one of the claims 1 to 11, characterised in that the sealing strips are elastic and heat-resistant and preferably consist of a rubber-like, heat-resistant material.

13. Heating chamber according to one of the claims 1 to 12, characterised in that sealing strips (35) form a pneumatic contact pressure zone on the back of a body (4), facing away from the closing surface, which contact pressure zone is subjected to the heating gas/saturated steam which is under operating pressure, the surface area of which zone is greater than the surface area of the heating region defined between the closing surfaces by the sealing strips (25).

14. Heating chamber according to claim 13, characterised in that the sealing strips (35) are inserted in grooves.

15. Heating chamber according to claim 14 and one of the claims 7 to 9, characterised in that the grooves and the sealing strips (25 and 35) inserted therein are arranged in the thread guiding body (6) on both sides of the vertical plane which is in the thread channel (10) and is perpendicular to the closing surfaces.

16. Heating chamber according to one of the claims 1 to 15, characterised in that the thread channel (10) is increased in width and/or depth in the middle region (19) where it is substantially greater in width and/or depth than at the thread inlet or thread outlet, the maximum width being the distance between the sealing strips (25).

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